JP5849271B2 - Single-shot air hammer tool and method of adjusting the striking force of the single-fire air hammer tool - Google Patents

Description

  The present invention relates to a single-shot air hammer tool in which a hammer reciprocates once in a single operation.

  Conventionally, as a hand-type impact tool, an air hammer tool using compressed air as a drive source is known. In such an air hammer tool, a hammer that can slide back and forth is arranged in a cylinder, and compressed air is introduced into the rear end side of the hammer in the cylinder, and the hammer advances to a chisel attached to the air hammer. Or directly impact the workpiece. Further, since it is necessary to form an airtight space before and after the hammer in the cylinder in order to enable the operation of the hammer, an airtight holding member such as packing is generally attached to the hammer. It is.

  For example, Patent Document 1 discloses an air beater in which a sealing ring is attached to a piston (hammer).

  In Patent Document 2, as a pneumatic nailing machine for driving a single nail using air pressure by a single operation, a cylindrical convex portion is formed on the back surface of a piston (hammer), and an outer peripheral surface of the convex portion. A piston rib is provided on the back side of the piston, and when the piston moves backward, the convex part of the piston engages the piston catch to hold the piston in the standby position, and pressurized air is supplied to the cylinder. Has been disclosed that the convex portion of the piston is detached from the piston catch and activated by air pressure. In this case, when the piston returns to the standby position, the piston convex part engages with the piston catch and the piston catch is restrained so as not to expand, so that the piston is always fixed at the standby position in the stationary state. Will be.

Japanese Patent Laid-Open No. 10-230474 Japanese Patent Laid-Open No. 2001-25980

  However, in the air beater disclosed in Patent Document 1, when the piston slides back and forth, the sealing ring always comes into contact with the inner peripheral surface of the cylinder (housing). Furthermore, the frictional force between the sealing ring and the inner circumferential surface of the cylinder acts as a resistance against the forward / backward sliding of the piston, particularly the forward movement, so-called loss is large, and a sufficient striking force cannot be obtained compared to a given air pressure. There was a problem.

  Further, in the pneumatic nailing machine disclosed in Patent Document 2, it is necessary to assemble the piston catch so that two states of an expandable state and an unexpandable state are obtained. There is a problem that the structure becomes complicated and the manufacturing cost becomes very high.

  SUMMARY OF THE INVENTION An object of the present invention is to provide a one-shot air hammer tool that can reduce the wear of a member as low as possible with a simple configuration and can convert the pressure of compressed air into a hammering force without waste.

  Another object of the present invention is to provide a striking force adjusting method that can suitably adjust the striking force in the air hammer tool.

The present invention is directed to a cylinder, a hammer disposed in the cylinder so as to be slidable back and forth, an operation switch for introducing compressed air into the cylinder, and the hammer attached to the front side of the cylinder hits the cylinder. A tip tool, and when the operation switch is operated once and compressed air is introduced into the cylinder, the hammer is arranged in front of the stop position from a stop position determined in the cylinder. advanced to the collision position to collide with been tip, after colliding with the tip again stops at the stop position to reverse towards the stop position, the striking force to the work W at the tip of the tip a single type of air hammer tool which gives a predetermined position facing the hammer located in the stop position a the inner circumferential surface of the cylinder, the elastic member, the cylinder at least partially A recess is provided at a position corresponding to the elastic member of the hammer located at the stop position, and the recess is locked to the elastic member. Due to the pressure of the compressed air introduced by operating the operation switch once, the hammer located at the stop position is urged forward, and the locking state between the recess and the elastic member in the hammer is When the hammer is released, the hammer starts moving forward, and the concave portion of the hammer that moves backward in the cylinder from the collision position toward the stop position is re-engaged with the elastic member, so that the hammer stops at the stop position. The elastic member is made of a metal material, is composed of a circular linear material having a circular longitudinal section, and is elastically deformed only in the radial direction by partially notching and forming a gap. do it Diameter becomes a partially cut annular member which is freely scaled, the inner peripheral surface of the cylinder, the recess in which the partially cut annular body is only elastically deformed freely housed in the radial direction is provided, said hammer The hammer is fitted in the ring of the partly cut-out annular body in the state of being in the stop position, and the hammer in the stop position is urged forward, When the cut surface shape of the linear member is cut along a plane including the central axis of the notched annular body, and the inner diameter of the partially notched annular body is expanded, the locked state is maintained. When the hammer is released from the partially-notched annular body and is moved backward and fitted to the partially-notched annular body again, the linear shape constituting the partially-notched annular body is released. The cut surface shape of the material does not deform, and the inner diameter of the partially cut annular body increases. This is a one-shot air hammer tool characterized by the above.

  With this configuration, it is possible to provide a one-shot air hammer tool with a simplified internal structure. In addition, a predetermined amount of compressed air is introduced into the cylinder until the elastic member is removed from the recess, and the hammer can be accelerated at a moment when the elastic member is removed from the recess. Sufficient hammering force can be secured. Furthermore, since the elastic member is arranged on the cylinder side and the hammer does not contact the hammer after passing the position where the elastic member is disposed, the speed of the hammer is reduced. It is possible to minimize the wear of the elastic member and the hammer while not hindering the ascent.

  Here, for example, in a use site such as a construction site or a factory, it is necessary to develop a sufficient striking force as an impact tool, so that the weight of the hammer may increase. If the O-ring or the like is configured, the cross-sectional shape of the O-ring or the like is easily deformed, and the hammer cannot be held at the stop position until a desired air pressure is reached. Sometimes. Further, for example, a rubber O-ring has a problem that, when expanded in the radial direction, the wire diameter becomes thin and the O-ring itself is easily broken.

  In view of this, the above-described configuration has been proposed in order to properly hold a heavy hammer at the stop position even when a high air pressure is applied. That is, when the elastic member is configured to be elastically deformed only in the radial direction without deforming the cross-sectional shape, the holding force of the hammer is remarkably increased. Specifically, when the hammer is detached from the partially cut annular body, the cross sectional shape of the partially cut annular body is not distorted in the traveling direction side of the hammer. Therefore, the force for holding the hammer at the stop position increases, and the hammer can be accelerated more instantaneously.

  In addition, it is preferable that the inner peripheral surface of the cylinder is provided with a concave portion in which the partially-notched annular body is accommodated in a radially deformable manner.

  By adopting such a configuration, it is possible to place the partially-notched annular body at a predetermined position with respect to the hammer that moves back and forth each time the operation switch is operated.

  The hit object is preferably a tip attached to the front side of the cylinder.

  With such a configuration, it is possible to perform work using a tip-shaped tip according to the purpose. Even if the tip of the tip is worn and needs to be replaced, only the tip needs to be replaced, so that the maintenance work for the entire air hammer tool becomes very easy.

  Moreover, it is preferable that the said elastic member is a metal partially notched annular body.

  By adopting such a configuration, it is possible to reliably prevent the cross-sectional shape of the partially notched annular body from being distorted in the traveling direction side of the hammer when the hammer is detached from the partially notched annular body. It becomes.

  Further, the present invention is a striking force adjustment method in the single-shot air hammer tool, wherein the position of the concave portion locked to the elastic member is changed along the axial direction of the hammer, A striking force adjusting method for a single air hammer tool characterized in that the striking force is changed.

  In such a configuration, when the position of the concave portion is changed, the length of time that the outer peripheral surface of the hammer and the elastic member come into contact with each other when the hammer moves forward changes. Will change. For this reason, for example, by changing the position of the concave portion, the contact time between the hammer and the elastic member is lengthened to suppress the speed at the time of the hammer advancement, or the contact time between the hammer and the elastic member is shortened at the time of the hammer advancement. Speed can be improved. Thereby, the optimal striking force in an air hammer tool can be set.

In addition, the hammering force of the hammer is changed by changing the depth of a recess provided in the inner peripheral surface of the cylinder, in which the partially cut annular body is elastically deformable in the radial direction. May be.

In such a configuration, by changing the depth of the concave portion, the movable range of expansion of the elastic member changes, so that the force for holding the hammer at the stop position can be changed based on the movable range. Thereby, the acceleration of the hammer at the moment when the elastic member and the hammer are separated can be changed, and as a result, the striking force can be adjusted.

The single-shot air hammer tool of the present invention reduces the impact time due to frictional resistance as much as possible because the contact time between the elastic member and the hammer for ensuring airtightness is reduced. The holding force for positioning the hammer at the stop position increases, and an appropriate striking force can be expressed.
The striking force adjusting method of the present invention is the above air hammer tool, and can finely adjust the striking force.

FIG. 5 is a longitudinal sectional view of an air hammer tool in a normal state in Reference Example 1. It is an air hammer tool in a normal state, and is an explanatory view showing the flow of air. It is a longitudinal cross-sectional view which shows an air hammer tool when an operation switch is operated. It is explanatory drawing which shows the flow of the air around a valve | bulb, (a) is before switch operation, (b) has shown after switch operation. It is explanatory drawing which shows the engagement state of a recessed part and an elastic member. It is a longitudinal cross-sectional view which shows an air hammer tool when a hammer advances. It is a longitudinal cross-sectional view of the air hammer tool which shows the movement of the hammer when pushing down the operation switch. It is a longitudinal cross-sectional view of the air hammer tool which shows the movement of the hammer at the time of canceling operation of an operation switch. It is a longitudinal cross-sectional view of the air hammer tool of Reference Example 2. It is a longitudinal cross-sectional view of the air hammer tool of Reference Example 3. The elastic member concerning an Example is shown, (a) is a top view, (b) is the sectional view on the AA line of (a). It is explanatory drawing which shows the engagement state of the recessed part and elastic member concerning an Example.

  Hereinafter, the example which actualized this invention is demonstrated in detail. In addition, this invention is not limited to the example shown below, A design change is possible suitably. Further, in the description, for convenience, the description will be made by defining the vertical and horizontal directions, but the present invention is not limited to such a direction. A single-shot air hammer tool 1 (hereinafter also simply referred to as “air hammer tool 1”) will be described with reference to FIGS. In addition, the arrow in a figure has shown the flow (direction which a pressure generate | occur | produces) of compressed air.

  As shown in FIG. 1, the air hammer tool 1 includes a substantially cylindrical tool body 2. A compressed air inlet 3 is provided at the rear end of the tool body 2, and compressed air can be introduced into the tool body 2 through the compressed air inlet 3.

  Further, a switch hole 4 formed so as to be orthogonal to the axial direction of the tool body 2 is formed in the tool body 2, and the switch hole 4 and the compressed air introduction port 3 communicate with each other. . The switch hole 4 is opened in the side wall of the tool body 2, and a pin-shaped operation switch 5 disposed in the switch hole 4 is attached so as to be able to protrude and retract in the vertical direction with the head exposed. It has been.

  A hook-shaped operation lever 30 is rotatably attached to the outer surface of the tool body 2, and the lower surface of the operation lever 30 and the head of the operation switch 5 are in contact with each other. When the operation lever 30 is turned up and down, the operation switch 5 moves up and down accordingly.

  Further, a substantially cylindrical cylinder 6 opened forward is disposed at a front position in the tool body 2. A valve 7 is loaded in the inner space between the rear end of the cylinder 6 and the operation switch 5 so as to be movable back and forth. A coil spring 8 oriented in the front-rear direction is disposed on the outer periphery of the valve 7, and the valve 7 is urged forward by the coil spring 8 and abuts against the cylinder 6 via an O-ring 20. Yes.

  Further, a hammer 9 is disposed in the cylinder 6 so as to be slidable back and forth. The hammer 9 has a large-diameter main body portion 9a and a small-diameter rod portion 9b inserted forward from the main body portion 9a. Here, the movement range of the hammer 9 will be described in detail. The position at which the hammer 9 is at the rearmost position in the cylinder 6 is set as a stop position α as shown in FIG. The position where the hitting force is applied is a collision position β as shown in FIG.

  Further, as shown in FIG. 1 and the like, a first ventilation hole 12 is provided in the side wall of the cylinder 6, and the first ventilation hole 12 is formed between the cylinder 6 and the tool body 2. The cylinder side chamber 15 is communicated with. An O-ring 13 that functions as a one-way valve is attached at a position where the first vent hole 12 is open so as to cover the first vent hole 12. Specifically, air can flow from the cylinder 6 to the cylinder side chamber 15 through the first vent hole 12, but conversely, air can flow from the cylinder side chamber 15 to the cylinder 6. Is disconnected.

  Further, a second vent hole 14 is provided on the side wall of the cylinder 6 and in a position ahead of the first vent hole 12. Similarly to the first vent hole 12, the second vent hole 14 communicates with the cylinder side chamber 15.

  Further, a stopper member 16 is attached to the front end portion of the cylinder 6, and a closing member 17 is attached to a position on the front side of the cylinder 6 and serving as the front end portion of the tool body 2. The stopper member 16 and the closing member 17 are respectively formed with guide holes 16a and 17a through which the rod portion 9b provided in the hammer 9 can be inserted. The rod hole 9b is always inserted into the guide holes 16a and 17a, so that the airtightness in the cylinder 6 is secured.

  The operation switch 5 includes a pair of upper and lower large diameter portions 5a and 5b having an outer diameter substantially the same as the inner diameter of the switch hole 4, and a small diameter portion 5c formed between the large diameter portions 5a and 5b. ing. Furthermore, an operation portion 5d that protrudes from the upper large diameter portion 5a toward the operation lever 30 is formed.

  In the tool body 2, a cylinder direction passage 18 is formed from the switch hole 4 to the cylinder 6 side, and a valve direction passage 19 is formed from the switch hole 4 to the valve 7 side. ing. Further, an O-ring 20 provided at the front end portion of the valve 7 faces the cylinder-direction passage 18 and can be converted into a closed state and an open state by the back-and-forth movement of the valve 7. Further, a through hole 7a formed along the front-rear direction is arranged at the center of the valve 7, and the through hole 7a is formed in the side wall of the tool body 2 and communicates with the external space. Communicated with.

  An O-ring 10 as an elastic member (rubber material) is provided on the inner peripheral surface of the cylinder 6 between the valve 7 and the first vent hole 12 along the circumferential direction of the cylinder 6. Is attached. Specifically, an O-ring housing groove 6a for attaching the O-ring 10 is formed on the inner peripheral surface of the cylinder 6, and the O-ring 10 is disposed in the O-ring housing groove 6a. In this arrangement, a part of the O-ring 10 protrudes into the cylinder 6.

  On the other hand, a groove 11 as a recess is formed in an annular shape on the outer peripheral surface of the hammer 9 along the circumferential direction of the hammer 9. When the hammer 9 is in the stop position, a part of the O-ring 10 enters the groove 11 and the hammer 9 is temporarily engaged with the cylinder 6.

  In the above configuration, as shown in FIGS. 1, 2, and 4 (a), the operation switch 5 is biased toward the operation lever 30 when the operation lever 30 is not operated normally. Further, the cylinder direction passage 18 and the valve direction passage 19 communicate with the compressed air inlet 3. On the other hand, the cylinder direction passage 18 is blocked from ventilating the cylinder 6 by the O-ring 20 of the valve 7. The valve direction passage 19 communicates with the space on the rear side of the valve 7.

  Then, as shown in FIGS. 3 and 4 (b), when the operation lever 30 is turned downward and the operation switch 5 is pushed in, the gap between the operation portion 5d and the switch hole 4 and the valve direction passage are shown. 19 communicates, and the compressed air in the valve direction passage 19 is discharged to the outside through the switch hole 4. As a result, a pressure difference is generated before and after the valve 7, and the valve 7 is moved backward by the compressed air existing in the cylinder direction passage 18. When the valve 7 moves backward, the cylinder direction passage 18 and the cylinder 6 communicate with each other, and the compressed air in the cylinder direction passage 18 is introduced into the cylinder 6. At this time, when the valve 7 moves backward, the communication between the through hole 7a of the valve 7 and the ventilation path 2a is blocked, and the ventilation becomes impossible.

  The hammer 9 is biased forward by the compressed air introduced into the cylinder 6. The hammer 9 is stopped until a predetermined pressure is reached because the groove 11 formed on the outer periphery of the hammer 9 is locked to the O-ring 10 of the cylinder 6 (see FIG. 5A). When the urging force acting on the hammer 9 is larger than the locking force between the groove 11 and the O-ring 10, the O-ring 10 is detached from the groove 11. (See FIG. 5 (b)), the hammer 9 starts to advance in the cylinder 6. At this time, until the hammer 9 passes through the position of the O-ring 10, the outer peripheral surface of the hammer 9 and the O-ring 10 are in contact, but the entire hammer 9 passes through the position of the O-ring 10. Then, the hammer 9 moves forward without receiving any resistance by the O-ring 10.

  In the process in which the hammer 9 moves forward, compressed air in front of the hammer 9 in the cylinder 6 passes through the first vent hole 12 and the second vent hole 14 as shown in FIG. It flows into the side chamber 15 and the internal pressure of the cylinder side chamber 15 is increased. On the other hand, the compressed air introduced from the compressed air introduction port 3 is set to a pressure value exceeding the internal pressure of the cylinder side chamber 15, and the propulsive force of the hammer 9 is ensured by the internal pressure difference. Then, the tip of the rod portion 9b of the hammer 9 that has moved forward collides with a workpiece (a hitting object) (not shown), and gives a hitting force to the workpiece.

  As shown in FIGS. 6 and 7, when the hammer 9 reaches the collision position β, the hammer 9 abuts against the stopper member 16, and the first ventilation hole 12 communicates with the inside of the cylinder 6 at this position. . At this time, even when the operation switch 5 is pushed in, the valve 7 is maintained in the retracted state due to the pressure of the compressed air in the cylinder 6, and the through hole 7a of the valve 7 and the ventilation path 2a are maintained. The blocking state is maintained. Further, since the compressed air in the cylinder 6 is introduced into the cylinder side chamber 15 through the first vent hole 12, the pressure difference before and after the hammer 9 is eliminated, and the hammer 9 stops at the collision position β. (See FIG. 7).

  Then, as shown in FIG. 8, when the operation lever 30 is rotated to project the operation switch 5 to return to the initial reference position, the compressed air introduction port 3 communicates with the valve direction passage 19. The valve 7 is moved forward by the pressure of the compressed air. Then, the through hole 7a of the valve 7 communicates with the ventilation path 2a, and the compressed air in the cylinder 6 is opened to the outside through the through hole 7a and the ventilation path 2a. As a result, the pressure of compressed air behind the hammer 9 in the cylinder 6 is reduced, and the compressed air stored in the cylinder side chamber 15 flows into the cylinder 6 through the second vent hole 14, and the hammer 9 Is pushed backwards. Since the O-ring 13 functioning as a one-way valve is attached to the first vent hole 12, compressed air flows into the cylinder 6 from the cylinder side chamber 15 through the first vent hole 12. It is blocked from doing.

  Then, the hammer 9 moves backward toward the stop position α, and starts decelerating by the resistance of the O-ring 10 from the point where the outer peripheral surface of the hammer 9 and the O-ring 10 start to interfere with each other. When the position reaches the position of the O-ring 10, the groove 11 is locked to the O-ring 10, and the hammer 9 stops again at the stop position α.

  With the above-described configuration, the internal structure of the air hammer tool 1 can be simplified. Further, since the hammer 9 can be accelerated at a stroke when the O-ring 10 comes out of the groove 11, a sufficient striking force of the hammer 9 can be ensured. Further, the O-ring 10 is disposed on the cylinder 6 side, and the O-ring 10 does not come into contact with the hammer 9 after the hammer 9 has passed the position where the O-ring 10 is disposed. Therefore, the frictional resistance does not hinder the speed increase of the hammer 9 and wear of the O-ring 10 and the hammer 9 can be minimized.

  Note that the embodiment can be changed as appropriate, and a configuration in which an operator can directly operate the operation switch 5 as appropriate may be employed. In addition, the number and position of the first vent holes 12 and the second vent holes 14 can be set as appropriate within a range where a single-shot mechanism can be achieved. Moreover, the shape dimensions of the groove 11 and the O-ring 10 can be freely set as appropriate.

  Further, as shown in FIG. 9, a tip attachment member 40 is disposed on the front side of the closing member 17, a tip tool 50 such as a chisel is attached thereto, and a rear end 50 a of the tip tool 50 is attached to the rod portion 9 b of the hammer 9. It is good also as a structure which strikes. With this configuration, it is possible to realize the air hammer tool 55 that applies a striking force to the workpiece W at the tip 50b of the tip tool 50.

  In addition, as shown in FIG. 10, it is possible to change the striking force by changing the position of the groove 61 that is a recess in the hammer 60 along the axial direction of the hammer 60. Specifically, when the groove 61 is set near the rear end of the hammer 60, the air hammer tool 65 has an outer peripheral surface of the hammer 60 and an O-ring 62 when the hammer 60 moves forward. The contact time is shortened, the resistance by the O-ring 62 is reduced, and the impact force is improved. On the contrary, if the groove 61 is arranged on the front side of the hammer 60, the contact time between the O-ring 62 and the hammer 60 when the hammer 60 moves forward becomes longer, and the resistance by the O-ring 62 increases and the impact is increased. Force is reduced. Further, it is possible to adjust the striking force by appropriately changing the amount of fitting between the O-ring 62 and the groove 61.

  Next, the air hammer tool 75 according to the present embodiment will be described with reference to FIGS. In addition, about the point which is common in the structure described so far, it is assumed that description is simplified or abbreviate | omitted and the same code | symbol is attached | subjected.

  As shown in FIG. 12, a concave groove 77 is formed along the circumferential direction on the outer peripheral surface of the hammer 76 according to the present embodiment. On the other hand, a housing groove 85 is provided on the inner peripheral surface of the cylinder 6 along the circumferential direction of the cylinder 6.

  Further, a partially cut-out annular body 80 as an elastic member is disposed in the housing concave groove 85. As shown in FIG. 11, the partially cut-out annular body 80 is made of a metal and circular wire 81 having a circular cross section, and is partially cut away to form a gap 82 to be elastic in the radial direction. The inner diameter can be expanded and contracted by deformation. In addition, the recessed part concerning this invention is comprised by the said accommodation recessed groove | channel 85 in which the said notch annular body 80 is accommodated elastically deformable to radial direction.

  In such a configuration, as shown in FIG. 12, in the state where the hammer 76 is located at the stop position α, the hammer 76 is fitted inside the ring of the partially cutout annular body 80 (FIG. 12 ( a)). That is, the groove 76 of the hammer 76 is engaged with the partially-notched annular body 80 so that the hammer 76 is positioned at the stop position α. When the hammer 76 is located at the stop position α, compressed air is introduced and the hammer 76 is urged forward.

  Further, when the urging force exceeds a predetermined magnitude, the linear member 81 is cut when cut along a plane including the central axis CL of the partially cut annular body 80 as shown in FIG. The cutting state (circular shape) is not deformed, and the inner diameter of the partially-notched annular body 80 is expanded, so that the locked state is released and the hammer 76 is detached from the partially-notched annular body 80. To do.

  On the other hand, when the hammer 76 is moved backward to fit into the partially-notched annular body 80 and locked again, the cross-sectional shape (circular) of the linear member 81 constituting the partially-notched annular body 80 is The inner diameter of the partially-notched annular body 80 is expanded without deformation. In addition, the rear end portion that first contacts the partially-notched annular body 80 in the process of being inserted into the partially-notched annular body 80 by the hammer 76 has a tapered shape whose outer diameter decreases toward the rear end. It is desirable to do.

  In other words, the partially cut-out annular body 80 made of metal as the elastic member in the above configuration can be elastically deformed only in the radial direction in the housing groove 85 without deformation of the cross-sectional shape. Therefore, in the state where the compressed air pressure is applied to the hammer 76 located at the stop position α, the partially cut annular body 80 is not distorted in the traveling direction of the hammer 76. The force held at the stop position α increases dramatically. Therefore, the hammer 76 can be accelerated more instantaneously.

  The cross-sectional shape of the linear member 81 in the partially cut-out annular body 80 is preferably a perfect circle from the viewpoint of securing strength, and the striking force may be adjusted by changing the wire diameter. Specifically, when the wire diameter is increased, the rigidity of the partially-notched annular body 80 is increased, the holding force is increased, the pressure of the compressed air can be increased, and the striking force can be increased. . On the other hand, if the wire diameter is reduced, the striking force can be reduced. Further, the striking force may be adjusted by changing the groove width or depth of the concave groove 77 of the hammer 76. Further, the striking force may be adjusted by changing the groove width or groove depth of the housing concave groove 85.

  In addition, the elastic member concerning this invention is not limited to the said Example, Other shapes and materials may be employ | adopted. For example, the partially cut annular body 80 is preferably made of metal, but may be made of another hard material such as hard plastic.

5 Operation switch 6 Cylinder 50 Tip tool 75 Single-shot air hammer tool 76 Hammer 77 Concave groove (concave part)
80 Partially cut annular body (elastic member)
81 Linear body 82 Gap 85 Housing groove (recess)
W Work α Stop position β Collision position

Claims (3)

A cylinder, a hammer arranged in the cylinder so as to be slidable back and forth, an operation switch for introducing compressed air into the cylinder, a tip attached to the front side of the cylinder and struck by the hammer, With
When the operation switch is operated once and compressed air is introduced into the cylinder, the hammer collides with a tip disposed in front of the stop position from a stop position determined in the cylinder. advanced to the collision position, the after colliding with tip, and stops again at the stop position to reverse towards the stop position, single-type air hammer tool to hit force to the workpiece W at the tip of the tip Because
An elastic member is disposed at a predetermined position on the inner peripheral surface of the cylinder facing the hammer positioned at the stop position so that at least a part thereof protrudes toward the inside of the cylinder, and the stop position A concave portion is provided at a position corresponding to the elastic member of the hammer located at the concave portion, and the concave portion is locked to the elastic member;
The hammer positioned at the stop position is urged forward by the pressure of the compressed air introduced by operating the operation switch once, and the recessed portion of the hammer and the elastic member are locked. Is released, and the hammer starts to move forward. Further, the concave portion of the hammer that moves backward in the cylinder from the collision position toward the stop position is re-engaged with the elastic member, so that the hammer is in the stop position. Is to stop,
The elastic member is
Made of a metal material, the longitudinal section is made of an annular linear material with a circular shape , part of which is cut out to form a gap, so that it is elastically deformed only in the radial direction so that the inner diameter can be expanded and contracted. It consists of a partially cut annular body,
The inner peripheral surface of the cylinder is provided with a recess in which the partially cut annular body is accommodated so as to be elastically deformable only in the radial direction,
The hammer is fitted in the ring of the partially cut annular body in a state where the hammer is located at the stop position,
When the hammer located at the stop position is urged forward, the cut surface shape of the linear material is deformed when the hammer is cut along a plane including the central axis of the partially cut annular body. And the inner diameter of the partially cut annular body is expanded to release the locked state, and the hammer is detached from the partially cut annular body,
When the hammer that moves backward fits into the partially-notched annular body and is locked again, the shape of the cut surface of the linear material constituting the partially-notched annular body is not deformed and the partially-notched annular body is deformed. Single-shot air hammer tool characterized in that the inner diameter of the body expands.   It is a striking force adjustment method in the single air hammer tool according to claim 1,
  The striking force of the single air hammer tool is characterized in that the striking force of the hammer is changed by changing the position of the recess that is locked to the elastic member along the axial direction of the hammer. Adjustment method.   It is a striking force adjustment method in the single air hammer tool according to claim 1,
  The hammer impact force is changed by changing the depth of a recess provided in the inner peripheral surface of the cylinder, in which the partially-notched annular body is elastically deformable in the radial direction. A striking force adjustment method for a single air hammer tool characterized by

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