JP2018130823A - Impact device, impact force adjustment method for impact device, and impact sound frequency adjustment method for impact device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an impact device capable of reducing a sound.SOLUTION: An impact device 1 comprises: a hammer 30 comprising a hammer body part 31 and a protrusion part 32 which extends from the hammer body part 31 to a tip side, and whose diameter is smaller than that of the hammer body part 31; and a chisel 20 with an insertion hole part 23 into which the protrusion part 32 is inserted, on an upper end 20c, and on which an air removal hole part 25 for communicating the insertion hole part 23 and an external part is provided. The hammer 30 repeatedly slides between a top dead point ε and a bottom dead point δ, and on the bottom dead point δ, only a tip end of the protrusion part 32 on the hammer 30 collides with a hole bottom part 24 of the insertion hole part 23 on the chisel 20, namely becomes in a colliding state, and on the top dead point ε, the tip end of the protrusion part 32 on the hammer 30 is positioned in the insertion hole part 23 on the chisel 20, and is separated from the hole bottom part 24, namely becomes in a non-colliding state.SELECTED DRAWING: Figure 4

Description

  The present invention can be applied to, for example, a rock drill, a concrete breaker, a suspension machine, a nailing machine, a rivet driving machine, a pile driving machine, a ground leveling machine, a compactor, a rammer, a tamper, a compactor, an asphalt or concrete leveling machine, or a so-called jet chisel. It is related with the impact apparatus applicable to things like this, the impact force adjusting method of an impact apparatus, and the impact sound frequency adjusting method of an impact apparatus.

  Conventionally, various impact devices as described above have been proposed (see, for example, Patent Document 1). For example, Patent Document 1 discloses an impact transmission tool that is pressed against a casting workpiece that flows sequentially by the operation of a work robot. When the chisel of the impact transmission tool moves in the cylinder direction, compressed air is discharged. A configuration is shown in which the exhaust port to be started is closed by the chisel and starts to start. In addition, since the structure disclosed in Patent Document 1 moves in a state in which the chisel is airtight with respect to the cylinder, the chisel and the cylinder are assembled precisely, and the chisel is in the cylinder direction. By making the structure to start only after moving, idle shots are prevented.

JP 2004-291125 A

  However, in the configuration of Patent Document 1, for example, casting sand that has been scattered during the operation of dropping the casting sand may adhere to the circumferential surface of the chisel and enter a minute gap around the chisel. As described above, when the sand casts around the chisel, the chisel cannot move properly in the cylinder direction, and the impact transmission tool does not start stably. For this reason, in practice, it has been difficult to use in a working environment in which dust or the like that drops such cast sand is scattered.

  Therefore, the present invention is an impact device that is safe without starting unexpectedly, and that is stably activated with the chisel being prevented from being bitten even in a work environment including dust, etc., an impact force adjusting method for the impact device, and An object of the present invention is to provide a method for adjusting the impact sound frequency of an impact device.

  The present invention has an impact device main body portion in which a downward pointing tool is held at the lower end, and an impact force obtained by press-fitting gas into the impact device main body portion is a target to be hit through the tip tool. The impact device main body is disposed in a cylindrical cylinder portion in which a vertically movable hammer is built, and below the cylinder portion, and the tip tool is attached to a predetermined tool. A tip holder holding portion that is movable up and down within a height range, a gas introduction port portion that is formed on a side wall of the cylinder portion, and introduces the press-fitted gas into the cylinder portion, and the gas introduction port portion The gas is introduced into the lower space of the hammer in the cylinder portion through the cylinder and the hammer starts to rise in the cylinder portion, and the hammer is caused to collide with the upper end of the tip tool from above. An upper end of the tip tool pressed against the hitting object is in contact with the hammer placed in the cylinder portion, and the hammer is placed in the cylinder portion. When the tip tool is pushed up and moved to the uppermost position in the tip tool holding part, the predetermined part of the tip tool and the predetermined part of the cylinder part come into contact with each other, and the gas introduction port part is below the hammer. An airtight high-pressure space is formed, and the hammer starts to rise so that the hammer and the tip can collide with each other, while the tip is located below the uppermost position; and When the peripheral surface of the hammer mounted on the tip implement closes the gas introduction port, a non-high pressure space communicating with outside air is formed below the hammer, and the hammer Ma is a percussion device, wherein a a standby state continues to close the gas inlet portion.

  In such a configuration, when the tip tool comes into contact with the hit target and the tip tool relatively rises to the uppermost position, the hammer and the tip tool start to collide for the first time and the impact device starts to be activated. For this reason, so-called idling is prevented, and the safety performance is extremely excellent. Further, according to the present invention, the function of selectively controlling the impact device in the drive state or standby state is realized by a structure in which a hammer in the cylinder portion opens and closes the gas introduction port portion. Therefore, since the chisel does not have a structure for opening and closing the gas introduction port as in the prior art, the tip tool does not need to be assembled precisely. For this reason, foreign matter such as cast sand is prevented from being caught by a sufficient gap provided between the tip tool holding portion and the periphery of the tip tool, and the driving state and the standby state are selectively selected. A configuration for state conversion can be obtained stably.

  Further, in the above configuration, the impact device main body portion has a cover body in which the cylinder portion is built, and the cover body includes an inner space portion into which the gas is press-fitted from the outside, A sliding body having a sliding body main body that can slide up and down relative to the cover body and a cylinder portion provided at a lower end of the sliding body main body, An upper coil spring that is vertically oriented between the upper end surface and the cover body, and an upper coil spring that is oriented vertically and interposed between the lower end surface of the sliding body and the cover body. Compressed air with improved airtightness between the upper end surface of the sliding body and the inner peripheral surface of the cover body opposed to the upper end surface in the inner space. An inflow chamber is formed, and an outside of the compressed air inflow chamber is formed. When the gas is pressed into the gas, the gas reaches the gas introduction port, the sliding body is lowered relative to the cover body by the pressure of the gas, and the lower coil spring is elastically compressed. Thus, it is preferable that the sliding body is urged upward and the sliding body is urged downward by the upper coil spring.

  In such a configuration, the driving state is generated while the sliding bodies are arranged between the lower coil spring and the upper coil spring in the elastic state. Here, the lower coil spring plays a role of receiving the sliding body pushed downward by the compressed air. On the other hand, the upper coil spring plays a role of further urging the sliding body downward while the sliding body is pushed downward. It plays an auxiliary role to stably press against the hit object. In addition, since the impact generated when the hammer in the sliding body collides with the tip and the inertia of the reciprocating hammer are suitably absorbed by the two coil springs, it is great for the operator holding the cover body. Vibration is difficult to be transmitted. In addition, when the gas is press-fitted into the compressed air inflow chamber, the cylinder part is lowered, so that it is possible to realize the function of bringing the tip tool close to the hitting object without providing a separate air cylinder structure. On the other hand, when the pressure of the compressed air inflow chamber is reduced by controlling the inflow of gas, the sliding body rises, and the tip is separated from the impact target. For this reason, when the impact device is assembled to the work robot, the tip tool and the hitting object can be brought close to or separated from each other with a simple structure.

  Moreover, it is good also as a structure which the said front-end | tip tool and the said hit | damage object press relatively, and the said drive state generate | occur | produces in the process in which the said sliding body descends relatively with respect to the said cover body.

  With such a configuration, the driving state can be generated before the sliding body is lowered to the lowest position, so that the working efficiency is dramatically improved.

  Further, the present invention has an impact device main body portion in which a forward-facing tip tool is held at the front end, and a striking force obtained by injecting gas into the impact device main body portion is struck through the tip tool. An impact device to be applied to an object, wherein the impact device main body portion is disposed in a cylindrical cylinder portion in which a hammer capable of moving back and forth is built in, and in front of the cylinder portion, and the tip tool is set in a predetermined manner. A tip end holding portion that is movably moved back and forth within a length range, a gas introduction port that is formed on a side wall of the cylinder portion, and introduces the press-fitted gas into the cylinder portion, and the gas introduction port When the gas is introduced into the front space of the hammer in the cylinder portion through the portion and the hammer starts to move backward in the cylinder portion, the hammer is moved to the rear end of the tip. A rear space of the hammer in the cylinder portion is formed with a high-pressure space higher than the outside air, and the rear end of the tip tool relatively pressed against the hit object The end is in contact with the hammer placed in the cylinder part, and the hammer is pushed backward against the pressure in the rear space in the cylinder part, so that the end in the tip holding part When the tip tool moves to a position, a predetermined part of the tip tool and a predetermined part of the cylinder portion come into contact with each other, and an airtight high-pressure space is formed in front of the hammer so that the gas inlet port faces. The hammer starts to move backward, and the hammer and the tip are in a driving state in which the hammer can collide, while the tip is positioned forward of the last position and the tip A non-high pressure space communicating with outside air is formed in the front space, which is in front of the hammer, when the peripheral surface of the hammer pressed against the gas inlet port portion is closed, and the hammer The impact device is characterized in that a high-pressure space higher in pressure than the outside air is formed in the rear space, which is the rear, and the hammer is in a standby state in which the gas introduction port portion is continuously closed.

  In such a configuration, when the tip tool comes into contact with the hit target and the tip tool relatively moves to the last position, the hammer and the tip tool start to collide for the first time and the impact device starts to be activated. For this reason, so-called idling is prevented, and the safety performance is extremely excellent. Further, according to the present invention, the function of selectively controlling the impact device in the drive state or standby state is realized by a structure in which a hammer in the cylinder portion opens and closes the gas introduction port portion. Therefore, since the chisel does not have a structure for opening and closing the gas introduction port as in the prior art, the tip tool does not need to be assembled precisely. For this reason, foreign matter such as cast sand is prevented from being caught by a sufficient gap provided between the tip tool holding portion and the periphery of the tip tool, and the driving state and the standby state are selectively selected. A configuration for state conversion can be obtained stably. Further, the impact device is not limited to being used with the tip end facing downward, and can be used even when the tip end is oriented sideways, for example.

  Further, in the above configuration, the impact device main body portion has a cover body in which the cylinder portion is built, and the cover body includes an inner space portion into which the gas is press-fitted from the outside, The inner space includes a sliding body main body that is slidable back and forth relative to the cover body, and a cylinder that is provided at a front end of the sliding body main body. A rear coil spring that is interposed between the rear end face and the cover body in the front-rear direction, and a rear coil spring that is interposed between the front end face of the sliding body and the cover body. Compressed air with improved airtightness between the rear end surface of the sliding body and the inner peripheral surface of the cover body facing the rear end surface in the inner space. An inflow chamber is formed, and an outside of the compressed air inflow chamber is formed. When the gas is pressed into the gas, the gas reaches the gas inlet port, the sliding body moves forward relative to the cover body by the pressure of the gas, and the front coil spring is elastically compressed. Thus, it is preferable that the sliding body is urged rearward and the sliding body is urged forward by the rear coil spring.

  In such a configuration, the driving state is generated while the sliding bodies are disposed between the front coil spring and the rear coil spring in the elastic state. Here, the front coil spring plays a role of receiving the sliding body pushed forward by the compressed air. On the other hand, the rear coil spring plays a role of further urging the sliding body forward in a state where the sliding body is pushed forward. It plays an auxiliary role to stably press the tool against the strike target. In addition, since the impact generated when the hammer in the sliding body collides with the tip and the inertia of the reciprocating hammer are suitably absorbed by the two coil springs, it is great for the operator holding the cover body. Vibration is difficult to be transmitted. In addition, when the gas is press-fitted into the compressed air inflow chamber, the cylinder portion moves forward, so that it is possible to realize the function of bringing the tip tool close to the hitting object without providing a separate air cylinder structure. On the other hand, when the pressure of the compressed air inflow chamber is reduced by controlling the inflow of gas, the sliding body moves backward, and the tip implement is separated from the hit target. For this reason, when the impact device is assembled to the work robot, the tip tool and the hitting object can be brought close to or separated from each other with a simple structure.

  Moreover, it is good also as a structure which the said driving | running state generate | occur | produces in the process in which the said sliding body moves relatively ahead with respect to the said cover body, the said tip implement and the said hit | damage target are pressed relatively.

  With such a configuration, the driving state can be generated before the sliding body moves to the foremost position, so that the working efficiency is dramatically improved.

  Further, the present invention is a method for adjusting the impact force of the impact device, wherein the impact force is adjusted by changing a reciprocating distance of the hammer by changing an axial length of the tip tool. This is a method for adjusting the impact force of the impact device.

  Here, for example, if a tip having a predetermined length is replaced with another tip having a long axial length and the reciprocating distance of the hammer is relatively shortened, the acceleration distance of the hammer is shortened and the striking force is reduced. On the other hand, if the tip having a predetermined length is replaced with another tip having a short axial length and the reciprocating distance of the hammer is relatively increased, the acceleration distance of the hammer is extended and the striking force is increased.

  Further, the present invention is a method for adjusting a striking sound frequency of the impact device, wherein a frequency of a striking sound with which the hammer strikes the tip tool is adjusted by changing an axial length of the tip tool. It is the impact sound frequency adjustment method of the impact device.

  In this way, by changing the tip tool to one with a long shaft length or to a short one, the frequency of the impact sound can be adjusted to specify the condition that produces the lowest noise in the work environment. It becomes possible.

  The impact device of the present invention has the effects that vibration and noise are drastically reduced and the structure is simple and lightweight, so that it can be manufactured at low cost and can be started safely and stably.

  Further, the impact force adjusting method of the impact device according to the present invention has an effect of easily adjusting the impact force of the impact device.

  Moreover, the impact sound frequency adjusting method of the impact device has an effect of easily adjusting the frequency of the impact sound.

It is explanatory drawing which shows an example of the usage type in an impact apparatus. It is a longitudinal cross-sectional view which shows the impact apparatus main-body part of a stop state. It is a partially cutaway sectional view showing a sliding body main body. It is a longitudinal cross-sectional view which shows the impact device main-body part in a standby state. It is a longitudinal cross-sectional view which mainly shows the cylinder part of a standby state. It is a longitudinal cross-sectional view which mainly shows the cylinder part until it reaches a drive state. It is a longitudinal cross-sectional view which mainly shows the cylinder part of a drive state. It is explanatory drawing which shows another Example. It is a longitudinal cross-sectional view which shows the standby state of the impact apparatus main-body part concerning a modification. A partially cut-out annular body is shown, (a) is a front view, (b) is a side view, and (c) is a cross-sectional view taken along line AA. It is explanatory drawing which shows the hammer of a temporary stop state. (A) is explanatory drawing which shows the partially-notched annular body in a temporary stop state, (b) is explanatory drawing which shows the completely annular body in a descent | fall state. It is explanatory drawing which shows the hammer in a descent | fall state. It is a longitudinal cross-sectional view which shows the impact apparatus main-body part of the stop state concerning another Example. It is a longitudinal cross-sectional view which mainly shows the cylinder part of the waiting state concerning other Examples. It is a longitudinal cross-sectional view which shows the impact apparatus main-body part of the standby state concerning another Example. It is a longitudinal cross-sectional view which mainly shows the cylinder part until it reaches the drive state concerning another Example. It is a longitudinal cross-sectional view which mainly shows the cylinder part of the drive state concerning another Example.

  Embodiments of an impact device according to the present invention will be described with reference to the accompanying drawings. Note that the present invention is not limited to the following embodiment, and can be appropriately changed in design without departing from the gist of the present invention.

  As shown in FIG. 1, the impact device 1 is a device using compressed air (gas), and an impact device main body 1A that generates a striking force by compressed air that is press-fitted from the outside, and the impact device main body 1A. And a downwardly facing chisel (tip tool) 20 that is extended downward. The impact device main body 1A is fixed to the tip of a so-called robot arm R, and the chisel 20 is pressed against the striking target W placed on the work table 100 by the operation of the robot arm R. The striking force is applied to the striking target W via the. Thereby, the operation | work which drops the cast sand adhering to the hit | damage target W is performed, for example.

First, the impact device body 1A will be described in detail with reference to FIG.
The impact device main body 1 </ b> A has a cover body 2. The cover body 2 is composed of a cylindrical body whose axial direction is the vertical direction, and an air inlet 4a for introducing compressed air from the outside is provided at the upper end portion of the cover body 2. Then, by operating a trigger portion (not shown), the supply of compressed air to the impact device body portion 1A can be controlled. A known mechanism is preferably employed as the compressed air introduction mechanism that allows the compressed air to be introduced into the cover body 2 from the outside by operating the trigger portion and allows the inflow of the compressed air to be controlled.

  The cover body 2 has an inner space 2a whose longitudinal direction is the vertical direction. In addition, a gas press-fitting portion 6 a for pressurizing compressed air into the inner space 2 a is provided on the peripheral wall of the upper end portion of the cover body 2. Further, a valve 5 is disposed in the gas press-fitting portion 6a. The compressed air introduced from the intake port 4 a flows into the inner space 2 a through the valve 5. Moreover, the gas discharge part 6b is provided in the surrounding wall of the lower end of the cover body 2, and the compressed air introduce | transduced in the cover body 2 can be discharged | emitted outside.

  Moreover, the sliding body 8 is loaded in the above-described inner space 2a so as to be slidable in the vertical direction. The sliding body 8 is made of a metal material, and has a cylindrical columnar sliding body main body 10 having a large diameter, and a cylindrical cylinder portion 11 that extends downward from the center of the lower end surface 10 a of the sliding body main body 10. ing. Furthermore, the cylinder part 11 protrudes partially downward from the cover body 2 through a cylinder part insertion hole 6 c opened at the lower end of the cover body 2. A bearing member 17 is inscribed at the inner edge of the cylinder portion delivery hole 6c, and the cylinder portion 11 is slidably held by the bearing member 17.

  A plurality of O-rings 12 are fitted on the outer peripheral surface of the sliding body main body 10. The O-ring 12 is in close contact with the inner peripheral surface of the cover body 2. A compressed air inflow chamber 7 with improved airtightness is formed between the sliding body 8 and the inner peripheral surface of the cover body 2 in the upper part of the inner space 2a.

  Further, an upper coil spring 91 (elastic body) oriented in the vertical direction is disposed in the compressed air inflow chamber 7. More specifically, the upper coil spring 91 is elastically compressed between the upper end surface 10b of the sliding body main body 10 and the end surface 16b formed on the inner peripheral surface of the cover body 2 located above the upper end surface 10b. It is inserted in the state. The elastic upper coil spring 91 biases the sliding body 8 downward.

  Further, a lower coil spring 92 (elastic body) is fitted on the outer periphery of the cylinder portion 11. More specifically, an annular spring stopper 16 is provided at the lower end portion of the cover body 2, and the lower coil spring 92 is oriented along the vertical direction in the upper direction of the annular spring stopper 16. It is interposed between the end surface 16a and the lower end surface 10a of the sliding body main body 10 and functions as a compression spring.

  Further, as shown in FIGS. 2 and 3 and the like, a plurality of gas flow paths are provided through the sliding body main body 10. And among these gas flow paths, the gas discharge relay part 13 is comprised by the gas flow path which connects the compressed air inflow chamber 7 and the gas discharge part 6b, and the compressed air inflow chamber 7 and the inside of the cylinder part 11 are comprised. The gas introduction part 14a is comprised by the gas flow path which connects.

Next, the cylinder part 11 will be described in detail with reference to FIG.
As shown in FIG. 5, the cylinder part 11 of the sliding body 8 has an outer cylinder part 11a. In addition, a supply / exhaust switching valve 14c is disposed at the base end (upper end) in the outer cylinder portion 11a. On the other hand, a tip tool holding part 18 is formed in the lower opening 8a formed at the lower end of the outer cylinder part 11a, and the chisel 20 in the tip tool holding part 18 has a predetermined height range with respect to the cylinder part 11. It is held so that it can move up and down. The tip holding part 18 will be described later.

Next, the chisel 20 will be described in detail.
As shown in FIG. 5, the chisel 20 is made of a metal material, has a tip tool main body 22, and has a pointed tip 20 a attached to the tip of the tip tool main body 22, and an intermediate portion of the tip tool main body 22. The substantially disc-shaped retaining part 20b is provided.

  A shaft portion 20e is coupled to the upper end portion of the tip portion 20a, and an O-ring 20f is attached to the shaft portion 20e. The shaft portion 20e is fitted into and fixed to a hole formed at the lower end of the distal end tool body 22. In addition, the front-end | tip part 20a can be replaced | exchanged suitably, when the axial part 20e is inserted / removed with respect to the front-end | tip tool main body 22. FIG.

  In addition, a portion below the retaining portion 20b in the tip tool main body 22 has a cylindrical shape. And the inside of the tip tool main body 22 is filled with the buffer material 21 which consists of fiber materials, for example, and noise reduction is aimed at by the fiber material. Furthermore, in the peripheral wall of the tip tool main body 22, a plurality of heat radiation holes 20d for preventing the buffer material 21 from obtaining heat energy and excessively rising in temperature are formed in the portion filled with the buffer material 21. However, it is of course possible to adopt a configuration in which the buffer material 21 is not filled and the heat dissipation hole 20d is not formed.

  Further, the tip holding part 18 for holding the chisel 20 has a cap-shaped chuck body 15. More specifically, the upper end 20c of the chisel 20 is inserted from the lower opening 8a of the outer cylinder portion 11a and inserted into the cylinder portion 11, and the tip tool insertion hole 15a through which the chisel 20 is inserted is the center. The chuck body 15 that is open is covered. In the state where the chuck body 15 is covered, the retaining portion 20b is held between the inner surface of the chuck body 15 and the distal end surface of the outer cylinder portion 11a so as to be movable up and down within a predetermined height range. The chuck body 15 and the lower end portion of the cylinder portion 11 are screwed through the attached O-ring 15b. Thereby, the chisel 20 is held without dropping from the cylinder part 11. A fine gap may be formed between the chuck body 15 and the chisel 20, and the inside of the chuck body 15 is a non-airtight space. The operation mode of the chisel 20 will be described later.

  Further, a hammer 30 made of a metal material is slidably loaded in the vertical direction in the outer cylinder portion 11a of the cylinder portion 11. In the hammer 30, the optimal size and weight are set as appropriate.

  Further, a gas introduction port portion 11b communicating with the space above the air supply / exhaust switching valve 14c is provided on the side wall of the outer cylinder portion 11a. Then, the hammer 30 moves up and down to selectively obtain a state in which the gas introduction port portion 11b is opened or a state in which the hammer 30 is closed by the side surface (circumferential surface). The operating state of the impact device 1 when the gas inlet 11b is opened or closed will be described later.

  In the impact device 1 described above, when not in use, the trigger portion (not shown) is operated to enter a stop state α in which compressed air is not introduced (see FIG. 2). In this stop state α, the sliding body 8 is positioned upward in the cover body 2, and the hammer 30 in the cylinder portion 11 is placed at the lowest position by its own weight as shown in FIG. The chisel 20 in 18 is placed in the lowest position by its own weight. The gas introduction port portion 11 b is closed by the side surface of the hammer 30.

  On the other hand, when the impact device 1 is used, the impact device main body 1A is arranged at a predetermined position by the robot arm R, and the trigger portion (not shown) is operated, so that the compressed air enters the gas press-in portion 6a. Accordingly, the valve 5 continues to be press-fitted into the compressed air inflow chamber 7 while preventing the backflow. As shown in FIG. 4, the sliding body 8 descends against the biasing force of the lower coil spring 92 due to the pressure increased in the compressed air inflow chamber 7.

  As shown in FIG. 4, when the sliding body 8 is pushed downward, the volume of the compressed air inflow chamber 7 is expanded, and the lower coil spring 92 is elastic between the spring stopper 16 and the sliding body main body 10. It contracts and it will be in the state which urges | biases the sliding body 8 upwards. At the same time, the upper coil spring 91 continues to urge the sliding body 8 downward in an elastic state. In such a configuration, the lower coil spring 92 provides a vibration absorption effect and a noise suppression effect. Further, the upper coil spring 91 supplements the pressure of the compressed air and appropriately presses the sliding body 8 downward to suppress the rebound of the sliding body 8 during driving, thereby stabilizing the impact force.

  Further, as shown in FIG. 6, the compressed air press-fitted into the cover body 2 is discharged from the gas discharge part 6 b to the outside of the cover body 2 through the gas discharge relay part 13 formed in the sliding body main body part 10. The At the same time, the compressed air press-fitted into the cover body 2 is introduced into the cylinder part 11 via the gas introduction part 14a of the sliding body main body part 10, and the compressed air reaches the gas introduction port part 11b. As described above, when the compressed air reaches the gas inlet 11b, the impact device 1 enters the standby state β. Even in such a state, the gas introduction port portion 11 b is closed by the side surface of the hammer 30.

  Here, as shown in FIG. 6, the chisel 20 abuts against and is pressed against the striking target W in the process in which the sliding body 8 descends as described above. Accordingly, the chisel 20 starts to push up the hammer 30 in the cylinder portion 11 with the upper end 20 c of the chisel 20 being in contact with the hammer 30.

  Then, when the chisel 20 moves to the uppermost position in the tip holding part 18 in the process of lowering the sliding body 8, the lower end of the hammer 30 pushed up as shown in FIG. The gas inlet 11b is opened above 11b. Here, when the chisel 20 is at the uppermost position in the distal end tool holding portion 18, the concave curved surface portion at the upper end portion of the retaining portion 20 b of the chisel 20 and the convex curve at the opening edge of the lower opening portion 8 a. The surface part comes into contact.

  When the gas inlet port 11b is opened as described above, compressed air flows out of the gas inlet port 11b below the hammer 30 to form an airtight high-pressure space 11c facing the gas inlet port 11b. The Then, the hammer 30 starts to rise due to the pressure difference between the upper and lower spaces in the hammer 30, and as a trigger, the flow direction is appropriately controlled by the supply / exhaust switching valve 14 c, and the hammer 30 repeatedly moves up and down repeatedly on the upper end 20 c of the chisel 20. A driving state γ in which the impact force continues to be applied is generated. The intake / exhaust structure 11d is configured by a structure including an air supply / exhaust switching valve 14c that repeatedly moves the hammer 30 up and down.

  In the above configuration, the cover body 2 held by the robot arm R and the sliding body 8 in which the hammer 30 for striking the chisel 20 is inserted are separated, and the cover body 2 and the sliding body are separated. Since the upper coil spring 91 and the lower coil spring 92 are interposed between the upper coil spring 91 and the lower coil spring 92, the impact generated when the hammer 30 collides with the chisel 20 and the inertia of the hammer 30 reciprocating are affected by the upper coil spring 91 and the lower coil spring. 92 is preferably absorbed. For this reason, vibration transmission to the robot arm R is effectively suppressed.

  Moreover, since the drive state (gamma) generate | occur | produces by the said structure until the sliding body 8 descend | falls to the lowest position, the working efficiency as the impact apparatus 1 is good.

  When the operation of applying the striking force is completed and the robot arm R raises the impact device main body 1A, the chisel 20 starts to descend relative to the cylinder portion 11 due to its own weight, and communicates with the outside. A non-high pressure space is formed below 30. Further, while the stopped hammer 30 as shown in FIG. 6 is mounted on the chisel 20, the gas inlet 11b is closed and the standby state β is restored. Therefore, the impact device 1 is prevented from so-called idling and is extremely excellent in safety performance. In addition, the above-described configuration does not require the chisel 20 to be precisely assembled by the tip holding portion 18, and foreign matter such as cast sand is not caught between the chisel 20 and the cylinder portion 11. The drive state γ and the standby state β stably and selectively change the state.

  Further, when the introduction of the compressed air is stopped in the standby state β, the compressed air inflow chamber 7 is reduced in pressure, and the sliding body 8 rises relative to the cover body 2 (stop state α). Therefore, in the impact device 1, the sliding body 8 is in the lower position during the operation, and on the other hand, when the operation is interrupted by operating the trigger portion, the impact device 1 is released from the pressure of the compressed air and the urging force of the lower coil spring 92 is applied. As a result, the sliding body 8 rises to the original position, and the chisel 20 can be separated from the hit object W.

  Further, a striking force adjustment method is proposed in which the striking force is adjusted by changing the reciprocating distance of the hammer 30 by changing the axial length of the chisel 20.

  Here, for example, when the chisel 20 having a predetermined length on the upper side of the retaining portion 20b is replaced with another chisel 20 having a longer length, the acceleration distance of the hammer 30 is relatively reduced. Is shortened and the striking force is reduced. On the other hand, when the chisel 20 whose upper portion has a predetermined length is replaced with another chisel 20 having a shorter portion and the reciprocating distance of the hammer 30 is relatively increased, the acceleration distance of the hammer 30 is extended and the striking force is increased. Becomes larger.

  In addition, a striking sound frequency adjusting method is proposed in which the axial length of the chisel 20 is changed to adjust the frequency of the striking sound with which the hammer 30 strikes the chisel 20.

  In this way, by changing the chisel 20 to a longer one or shorter one, the frequency of the impact sound generated when the chisel 20 and the hammer 30 collide is adjusted. It becomes possible to specify the conditions that produce the lowest noise in the environment.

  The chisel 20 is, for example, a tipping tool for a rock drill, a concrete breaker or a lifting machine, a nail, a rivet or a pile for a nailing machine, a rivet driving machine or a pile driving machine, a leveling machine, a compactor, a rammer, a tamper, a rolling machine. If it is a pressure machine or leveling machine, it may be a plate that smoothes the ground, and if it is a jet chisel, it may be a needle bundle. Moreover, the gas press-fitted into the impact device 1 is not limited to compressed air, and may be a gas such as an inert gas.

  Further, as shown in FIG. 8, a support body 40 composed of a known bearing member is disposed in the cover body 2, and the support body 40 comes into contact with the side surface portion of the slide body 8 to slide the slide body. It is good also as the impact apparatus main-body part 1B which supports 8 so that a vertical movement is possible, and prevents the sliding body 8 from rattling.

  Further, an impact device 110 having a single-shot structure employing a hammer 130 described below instead of the above-described hammer 30 will be described with reference to FIG.

  As shown in FIG. 9, an accommodation concave groove 185 is formed in a circumferential shape on the inner peripheral surface of the outer cylinder portion 11 a and between the supply / exhaust switching valve 14 c and the gas introduction port portion 11 b. . A partially-notched annular body 180 as an elastic member (metal material) is attached to the housing concave groove 185 along the circumferential direction of the cylinder portion 11.

  More specifically, as shown in FIG. 10, the partially-notched annular body 180 is formed of a metal and circular wire 181 having a circular cross section, and a part is notched to form a gap 182. In the housing concave groove 185, the inner diameter can be expanded and contracted by elastic deformation in the radial direction. The partially cut ring 180 is preferably made of metal, but may be other hard material such as hard plastic.

  Then, as shown in FIG. 9, the arrangement is such that a part of the notched annular body 180 protrudes into the cylinder portion 11 in a state where the partially notched annular body 180 is disposed in the housing groove 185. ing.

  On the other hand, a groove 137 as a recess is formed in an annular shape on the outer peripheral surface of the hammer 130 along the direction around the axis of the hammer 130.

  Then, as described above, the chisel 20 abuts against the strike target W in the process of lowering the sliding body 8, the upper end of the chisel 20 pushes up the hammer 130, and the gas introduction port portion 11 b is opened. Is raised, the hammer 130 is once fitted into the notched annular body 80 and locked. At this time, the cross-sectional shape (circular shape) of the linear member 181 constituting the partially-notched annular body 180 is not deformed, and the inside diameter of the partially-notched annular body 180 is increased. It should be noted that the upper end portion that first contacts the partially-notched annular body 180 in the process of being inserted into the partially-notched annular body 180 by the hammer 130 may have a tapered shape whose outer diameter decreases toward the upper end.

  As shown in FIGS. 11 and 12A, a part of the partially cut annular body 180 enters the groove 137 and the hammer 130 is temporarily stopped with respect to the cylinder part 11.

  Next, when compressed air is introduced into the cylinder portion 11 from above while the hammer 130 is temporarily stopped, the hammer 130 is urged downward. Further, when the urging force exceeds a predetermined magnitude, the cut surface of the linear member 181 when cut along a plane including the central axis CL of the partially cut-out annular body 180 as shown in FIG. When the shape (circular shape) is not deformed and the inner diameter of the partially-notched annular body 180 is increased, the locked state is released, and the hammer 130 is detached from the partially-notched annular body 180. As a result, as shown in FIG. 13, the hammer 130 instantaneously starts moving downward in the cylinder portion 11. At this time, until the hammer 130 passes through the position of the partially-notched annular body 180, the outer peripheral surface of the hammer 130 and the partially-notched annular body 180 are in contact with each other. When passing the position, the hammer 130 is lowered without receiving any resistance due to the partially cut annular body 180. Then, the hammer 130 collides with the chisel 20 and generates a striking force in a single shot.

  In the above configuration, the hammer 130 can be accelerated at a moment when the partially cut annular body 180 comes out of the groove 137, so that the striking force of the hammer 130 can be sufficiently secured. Further, the partially-notched annular body 180 is disposed on the cylinder part 11 side, and after the hammer 130 passes through the position where the partially-notched annular body 180 is disposed, the partially-notched annular body 180 is connected to the hammer 130. Since there is no contact, frictional resistance does not hinder the increase in the speed of the hammer 130, and wear of the partially cut annular body 180 and the hammer 130 can be minimized.

  In addition, the present invention is not limited to transmitting the impact from the top to the bottom with respect to the strike target W like the above-described impact device 1, but may be configured to transmit the impact in the lateral direction, for example. Hereinafter, the impact device 200 will be described with reference to FIGS. In the impact device body 1C, the front end side of the chisel 20 is the front side, and the opposite side is the rear side. Also, components having the same configuration as the above-described impact device 1 will be described with the same reference numerals.

  The impact device 200 is a device that uses compressed air (gas), and the impact device main body 1C that generates a striking force by compressed air that is press-fitted from the outside, and the impact device main body 1C are pushed forward. A horizontal chisel (tip tool) 20 is provided. As with the impact device 1 shown in FIG. 1, the impact device main body 1 </ b> C is fixed to the tip of a so-called robot arm R, and the impact target W placed on the work table 100 by operating the robot arm R. The chisel 20 is pressed against the hit subject W, and the hitting force is applied to the hit target W via the chisel 20. Thereby, the operation | work which drops the cast sand adhering to the hit | damage target W is performed, for example.

First, the impact device body 1C will be described in detail with reference to FIG.
The impact device main body 1 </ b> C has a cover body 2. The cover body 2 is composed of a cylindrical body whose axial direction is the vertical direction, and an intake port 4a for introducing compressed air from the outside is provided at the rear end portion of the cover body 2. And by operating the trigger part which is not shown in figure, supply of the compressed air to the impact apparatus main-body part 1C is controllable. A known mechanism is preferably employed as the compressed air introduction mechanism that allows the compressed air to be introduced into the cover body 2 from the outside by operating the trigger portion and allows the inflow of the compressed air to be controlled.

  The cover body 2 has an inner space 2a whose longitudinal direction is the front-rear direction. Further, a gas press-fitting portion 6a for press-fitting compressed air into the inner space 2a is provided on the peripheral wall of the rear end portion of the cover body 2. Further, a valve 5 is disposed in the gas press-fitting portion 6a. The compressed air introduced from the intake port 4 a flows into the inner space 2 a through the valve 5. Further, a gas discharge portion 6b is provided on the peripheral wall at the front end of the cover body 2, so that compressed air introduced into the cover body 2 can be discharged to the outside.

  Moreover, the sliding body 8 is loaded in the above-described inner space 2a so as to be slidable in the vertical direction. The sliding body 8 is made of a metal material, and includes a cylindrical sliding body body 10 having a large diameter, and a cylindrical cylinder section 11 that extends forward from the center of the front end surface 210a of the sliding body body 10. ing. Further, the cylinder portion 11 is partially protruded forward from the cover body 2 through a cylinder portion outlet hole 6 c opened at the front end of the cover body 2. A bearing member 17 is inscribed at the inner edge of the cylinder portion delivery hole 6c, and the cylinder portion 11 is slidably held by the bearing member 17.

  A plurality of O-rings 12 are fitted on the outer peripheral surface of the sliding body main body 10. The O-ring 12 is in close contact with the inner peripheral surface of the cover body 2. A compressed air inflow chamber 7 with improved airtightness is formed between the sliding body 8 and the inner peripheral surface of the cover body 2 at the rear portion of the inner space 2a.

  Further, a rear coil spring 291 (elastic body) oriented in the front-rear direction is disposed in the compressed air inflow chamber 7. More specifically, the rear coil spring 291 is elastic between the rear end surface 210b of the sliding body main body 10 and the end surface 16b formed on the inner peripheral surface of the cover body 2 located behind the rear end surface 210b. It is inserted in a contracted state. The elastically compressed rear coil spring 291 biases the sliding body 8 forward.

  Further, a front coil spring 292 (elastic body) is fitted on the outer periphery of the cylinder portion 11. More specifically, an annular spring stop 16 is provided at the front end of the cover body 2, and the front coil spring 292 is oriented along the front-rear direction and the rear end surface of the annular spring stop 16. It is interposed between 216a and the front end surface 210a of the sliding body main body 10, and functions as a compression spring.

  Further, as shown in FIGS. 2 and 3 and the like, a plurality of gas flow paths are provided through the sliding body main body 10. And among these gas flow paths, the gas discharge relay part 13 is comprised by the gas flow path which connects the compressed air inflow chamber 7 and the gas discharge part 6b, and the compressed air inflow chamber 7 and the inside of the cylinder part 11 are comprised. The gas introduction part 14a is comprised by the gas flow path which connects.

Next, the cylinder part 11 will be described in detail with reference to FIG.
As shown in FIG. 15, the cylinder part 11 of the sliding body 8 has the outer cylinder part 11a. In addition, a supply / exhaust switching valve 14c is disposed at a base end portion (rear end portion) in the outer cylinder portion 11a. On the other hand, a front end holding part 18 is formed in a front opening 208a formed at the front end of the outer cylinder part 11a. It is held so that it can move back and forth. The tip holding part 18 will be described later.

Next, the chisel 20 will be described in detail.
As shown in FIG. 15, the chisel 20 is made of a metal material, has a tip tool main body 22, and has a pointed tip 20 a attached to the tip of the tip tool main body 22 and an intermediate portion of the tip tool main body 22. The substantially disc-shaped retaining part 20b is provided.

  A shaft portion 20e is coupled to the rear end portion of the tip portion 20a, and an O-ring 20f is attached to the shaft portion 20e. The shaft portion 20e is fitted and fixed in a hole formed at the front end of the distal end tool body 22. In addition, the front-end | tip part 20a can be replaced | exchanged suitably, when the axial part 20e is inserted / removed with respect to the front-end | tip tool main body 22. FIG.

  In addition, the front part of the distal end tool main body 22 from the retaining part 20b has a cylindrical shape. And the inside of the tip tool main body 22 is filled with the buffer material 21 which consists of fiber materials, for example, and noise reduction is aimed at by the fiber material. Furthermore, in the peripheral wall of the tip tool main body 22, a plurality of heat radiation holes 20d for preventing the buffer material 21 from obtaining heat energy and excessively rising in temperature are formed in the portion filled with the buffer material 21. However, it is of course possible to adopt a configuration in which the buffer material 21 is not filled and the heat dissipation hole 20d is not formed.

  Further, the tip holding part 18 for holding the chisel 20 has a cap-shaped chuck body 15. More specifically, the rear end 220c of the chisel 20 is inserted from the front opening 208a of the outer cylinder portion 11a and inserted into the cylinder portion 11, and the tip tool insertion hole 15a through which the chisel 20 is inserted is the center. The chuck body 15 that is open is covered. In the state where the chuck body 15 is covered, the retaining portion 20b is held movably back and forth within a predetermined length range between the inner surface of the chuck body 15 and the front end surface of the outer cylinder portion 11a, and is attached to the outer periphery of the cylinder portion 11. The chuck body 15 and the front end portion of the cylinder portion 11 are screwed together via the attached O-ring 15b. Thereby, the chisel 20 is held without dropping from the cylinder part 11. A fine gap may be formed between the chuck body 15 and the chisel 20, and the inside of the chuck body 15 is a non-airtight space. The operation mode of the chisel 20 will be described later.

  A hammer 30 made of a metal material is loaded in the outer cylinder portion 11a of the cylinder portion 11 so as to be slidable in the front-rear direction. In the hammer 30, the optimal size and weight are set as appropriate.

  Further, a gas introduction port portion 11b communicating with the space above the air supply / exhaust switching valve 14c is provided on the side wall of the outer cylinder portion 11a. Then, the hammer 30 moves up and down to selectively obtain a state in which the gas introduction port portion 11b is opened or a state in which the hammer 30 is closed by the side surface (circumferential surface). The operating state of the impact device 1 when the gas inlet 11b is opened or closed will be described later.

  Furthermore, in the outer cylinder part 11a in the cylinder part 11, the rear space 11e behind the hammer 30 is formed with a high-pressure space that is higher in pressure than the outside air.

  In the above-described impact device 200, when not in use, the trigger portion (not shown) is operated to enter a stop state α in which compressed air is not introduced (see FIG. 14). In this stop state α, the sliding body 8 is positioned rearward in the cover body 2, and the hammer 30 in the cylinder portion 11 is positioned at the foremost position because the rear space 11e is a high-pressure space as shown in FIG. The chisel 20 in the tip holding part 18 is pushed by the hammer 30 and is urged to be positioned at the foremost position. The gas introduction port portion 11 b is closed by the side surface of the hammer 30.

  On the other hand, when the impact device 200 is used, the impact device main body 1C is arranged at a predetermined position by the robot arm R, and the trigger portion (not shown) is operated, so that the compressed air enters the gas press-fit portion 6a. Accordingly, the valve 5 continues to be press-fitted into the compressed air inflow chamber 7 while preventing the backflow. As shown in FIG. 16, the sliding body 8 moves forward against the urging force of the front coil spring 292 due to the pressure increased in the compressed air inflow chamber 7.

  As shown in FIG. 16, when the sliding body 8 is pushed forward, the volume of the compressed air inflow chamber 7 is expanded, and the front coil spring 292 is elastically contracted between the spring stopper 16 and the sliding body main body 10. Thus, the sliding body 8 is biased backward. At the same time, the rear coil spring 291 continues to urge the sliding body 8 forward in an elastic state. In such a configuration, a vibration absorption effect and a noise suppression effect are obtained by the front coil spring 292. In addition, the rear coil spring 291 supplements the pressure of the compressed air and appropriately presses the sliding body 8 forward to suppress the rebound of the sliding body 8 during driving, thereby stabilizing the impact force.

  In addition, as shown in FIG. 17, the compressed air press-fitted into the cover body 2 is discharged from the gas discharge portion 6 b to the outside of the cover body 2 through the gas discharge relay portion 13 formed in the slide body main body portion 10. The At the same time, the compressed air press-fitted into the cover body 2 is introduced into the cylinder part 11 via the gas introduction part 14a of the sliding body main body part 10, and the compressed air reaches the gas introduction port part 11b. As described above, when the sliding body 8 is pushed forward and the compressed air reaches the gas introduction port portion 11b, the impact device 1 enters the standby state β. Even in such a state, the gas introduction port portion 11 b is closed by the side surface of the hammer 30.

  Here, as shown in FIG. 17, the chisel 20 abuts against the striking object W and is pressed in the process of moving the sliding body 8 forward as described above. Accordingly, the chisel 20 starts to push the hammer 30 backward in the cylinder portion 11 while the rear end surface 220c of the chisel 20 is in contact with the hammer 30.

  Then, when the chisel 20 moves to the last position in the tip holding part 18 in the process of moving the sliding body 8 forward, the front end of the hammer 30 pushed in as shown in FIG. The gas inlet 11b is opened at the rear of the portion 11b. Here, at the position where the chisel 20 is the last position in the tip tool holding portion 18 portion, the concave curved surface portion at the rear end portion of the retaining portion 20b of the chisel 20 and the convex curve at the opening edge of the front opening portion 208a. The surface part comes into contact.

  When the gas inlet port 11b is opened as described above, compressed air flows out from the gas inlet port 11b in front of the hammer 30, and an airtight high-pressure space 11c facing the gas inlet port 11b is formed. The Then, the hammer 30 starts to move backward due to the pressure difference between the upper and lower spaces in the hammer 30. With this as the trigger, the flow direction is appropriately controlled by the supply / exhaust switching valve 14c, the hammer 30 repeatedly moves back and forth, and the rear end surface 220c of the chisel 20 A driving state γ is generated in which the impact force continues to be applied by repeatedly colliding with each other. The intake / exhaust structure 11d is configured by a structure including an air supply / exhaust switching valve 14c that repeatedly moves the hammer 30 back and forth.

  In the above configuration, the cover body 2 held by the robot arm R and the sliding body 8 in which the hammer 30 for striking the chisel 20 is inserted are separated, and the cover body 2 and the sliding body are separated. 8, the rear coil spring 291 and the front coil spring 292 are interposed therebetween, so that the impact generated when the hammer 30 collides with the chisel 20 and the inertia of the hammer 30 reciprocating are affected by the rear coil spring 291 and the front coil spring. 292 is preferably absorbed. For this reason, vibration transmission to the robot arm R is effectively suppressed.

  Moreover, since the drive state (gamma) generate | occur | produces by the said structure until the sliding body 8 moves to the foremost position, the working efficiency as the impact apparatus 1 is good.

  Then, when the operation of applying the striking force is completed and the robot arm R raises the impact device main body 1C, the chisel 20 starts to move forward relative to the cylinder portion 11 by the pressure of air in the rear space 11e. A non-high pressure space is formed below the hammer 30 by communicating with the outside. Further, the gas introduction port portion 11b is closed while the stopped hammer 30 as shown in FIG. Therefore, the impact device 200 is prevented from so-called idling and is extremely excellent in safety performance. In addition, the above-described configuration does not require the chisel 20 to be precisely assembled by the tip holding portion 18, and foreign matter such as cast sand is not caught between the chisel 20 and the cylinder portion 11. The drive state γ and the standby state β stably and selectively change the state.

  Further, when the introduction of the compressed air is stopped in the standby state β, the compressed air inflow chamber 7 is reduced in pressure, and the sliding body 8 moves rearward relative to the cover body 2 (stop state α). Therefore, in the impact device 200, the sliding body 8 is in the forward position during the operation, and on the other hand, when the operation is interrupted by operating the trigger portion, the impact device 200 is released from the pressure of the compressed air and is applied by the urging force of the front coil spring 292. The sliding body 8 moves backward to the original position, and the chisel 20 can be separated from the hit object W. In the above-described stop state α, for example, even if the chisel 20 is directed upward, the hammer 30 is positioned at the foremost position in the cylinder portion 11 because the rear space 11e is a high-pressure space higher in pressure than the outside air. It is maintained as it is.

1,200 Impact device 1A, 1B, 1C Impact device body 2 Cover body 2a Inner space 7 Compressed air inflow chamber 8 Slide body 10 Slide body body 11 Cylinder 11b Gas inlet 11d Intake / exhaust structure 11e Rear space 18 Tip tool holding part 20 Chisel (tip tool)
30 Hammer 91 Upper coil spring 92 Lower coil spring 291 Rear coil spring 292 Front coil spring W Strike target β Standby state γ Drive state

Claims (8)

An impact that has an impact device main body having a downward-pointing tip held at the lower end, and applies a striking force obtained by press-fitting gas into the impact device main body to the impact target via the tip A device,
The impact device main body includes a cylindrical cylinder portion in which a vertically movable hammer is incorporated,
A tip tool holding part that is disposed below the cylinder part and holds the tip tool in a predetermined height range so as to be movable up and down;
Formed on the side wall of the cylinder portion, and a gas introduction port portion for introducing the press-fitted gas into the cylinder portion;
The hammer collides with the upper end of the tip tool from above when the gas is introduced into the lower space of the hammer in the cylinder portion through the gas introduction port portion and the hammer starts to rise in the cylinder portion. Intake and exhaust structure
Comprising
An upper end of the tip tool relatively pressed against the hitting object is in contact with the hammer placed in the cylinder part, and the hammer is pushed up in the cylinder part and the tip tool holding part When the tip tool moves to the uppermost position, a predetermined part of the tip tool and a predetermined part of the cylinder part come into contact with each other, and an airtight high-pressure space where the gas introduction port part faces below the hammer is formed. Then, the hammer starts to rise and enters a driving state in which the hammer and the tip can collide,
On the other hand, when the tip tool is located below the uppermost position and the peripheral surface of the hammer mounted on the tip tool closes the gas inlet port, the outside air is placed below the hammer. The impact device is characterized in that a non-high pressure space communicating with the gas is formed, and the hammer is in a standby state in which the gas introduction port portion is continuously closed. The impact device body is
A cover body in which the cylinder portion is built;
The cover body is
Comprising an inner space into which the gas is injected from the outside,
In the inner space,
A sliding body having a sliding body main body that can slide up and down relatively with respect to the cover body, and the cylinder provided at a lower end of the sliding body main body;
An upper coil spring interposed between the upper end surface of the sliding body and the cover body, oriented in the vertical direction;
In addition, a lower coil spring is disposed between the lower end surface of the sliding body and the cover body so as to be oriented in the vertical direction.
Further, a compressed air inflow chamber with improved airtightness is formed between the upper end surface of the sliding body and the inner peripheral surface of the cover body facing the upper end surface in the inner space,
When the gas is pressed into the compressed air inflow chamber from the outside, the gas reaches the gas inlet port, and the sliding body is lowered relative to the cover body by the pressure of the gas, 2. The impact device according to claim 1, wherein the lower coil spring is elastically urged to urge the sliding body upward, and the sliding body is urged downward by the upper coil spring. The impact device according to claim 2, wherein the driving state is generated by pressing the tip tool and the hitting object relatively in a process in which the sliding body descends relative to the cover body. An impact that has an impact device main body portion that has a forward-facing tip tool held at the front end, and that imparts a striking force obtained by press-fitting gas into the impact device main body portion to an impact target via the tip tool. A device,
The impact device main body includes a cylindrical cylinder portion in which a hammer that can move back and forth is built-in,
A tip tool holding part that is disposed in front of the cylinder part and holds the tip tool in a predetermined length range so as to be movable back and forth; and
Formed on the side wall of the cylinder portion, and a gas introduction port portion for introducing the press-fitted gas into the cylinder portion;
When the gas is introduced into the front space of the hammer in the cylinder portion through the gas introduction port portion and the hammer starts to move backward in the cylinder portion, the hammer is moved to the rear end of the tip tool. An intake / exhaust structure for collision from the side,
Comprising
The space behind the hammer in the cylinder part is formed with a high-pressure space that is higher than the outside air,
A rear end of the tip tool pressed relatively to the hit object is in contact with the hammer placed in the cylinder portion, and the hammer is subjected to pressure in the rear space in the cylinder portion. When the tip is moved backward to the last position in the tip holder holding portion, the predetermined part of the tip and the predetermined part of the cylinder part come into contact with each other, and the front part of the hammer is in front of the hammer. An airtight high-pressure space facing the gas inlet port is formed, the hammer starts to move backward, and the hammer and the tip end are in a driving state in which they can collide,
On the other hand, when the tip is located in front of the last position and the peripheral surface of the hammer pressed against the tip closes the gas inlet port, the tip is in front of the hammer. A non-high pressure space communicating with the outside air is formed in the front space, and a high pressure space higher in pressure than the outside air is formed in the rear space behind the hammer, and the hammer closes the gas introduction port portion. An impact device characterized by being in a standby state to continue. The impact device body is
A cover body in which the cylinder portion is built;
The cover body is
Comprising an inner space into which the gas is injected from the outside,
In the inner space,
A sliding body having a sliding body main body that can slide back and forth relative to the cover body and the cylinder portion provided at a front end of the sliding body main body;
A rear coil spring that is interposed between the rear end surface of the sliding body and the cover body so as to be oriented in the front-rear direction;
In addition, a front coil spring is disposed between the front end face of the sliding body and the cover body and is oriented in the front-rear direction, and is disposed.
Further, a compressed air inflow chamber with improved airtightness is formed between the rear end surface of the sliding body and the inner peripheral surface of the cover body facing the rear end surface in the inner space portion,
When the gas is pressed into the compressed air inflow chamber from the outside, the gas reaches the gas inlet port, and the sliding body moves forward relative to the cover body by the pressure of the gas. 5. The impact device according to claim 4, wherein the sliding body is biased rearward by the elastic contraction of the front coil spring, and the sliding body is biased forward by the rear coil spring. The impact device according to claim 5, wherein the driving state is generated by pressing the tip tool and the hitting target relatively in a process in which the sliding body moves forward relative to the cover body. The impact force adjusting method for an impact device according to any one of claims 1 to 6,
A striking force adjustment method for an impact device, wherein the striking force is adjusted by changing the reciprocating distance of the hammer by changing the axial length of the tip tool. The impact sound frequency adjusting method for an impact device according to any one of claims 1 to 6,
A method for adjusting a striking sound frequency of an impact device, comprising: changing a shaft length of the tip tool to adjust a frequency of a striking sound with which the hammer strikes the tip tool.

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