JP2017087414A - Driving tool - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enhance the durability of a rack pinion mechanism in the case where a driving tool keeps driving reaction reduced by moving a weight reversely to a driving direction with the rack pinion mechanism, and where a deviation between the timing of an impact driver to reach an advancement end and the timing of the weight to reach a retreat end causes durability spoilage under the application of unreasonable external force on meshing teeth of the rack pinion mechanism.SOLUTION: A rack pinion mechanism 80 is provided with a drive side pinion gear 83 and a driven side pinion gear 86 to be rotatable relatively in coaxiality with each other over a constant angle range. This manner prevents an unreasonable external force from being applied on meshing teeth 81a, 82a by the relative rotation of both the pinion gears 83, 86 to enhance the durability of the rack pinion mechanism 80 when the timing of an impact driver 3 to reach an advancement end and the timing of a weight 5 to reach a retreat end deviate from each other.SELECTED DRAWING: Figure 4

Description

  The present invention relates to a driving tool such as a rechargeable pin tacker.

  In addition to tools that use the thrust of a compressed air driven cylinder as the driving force, tools that use the biasing force of the compression spring as the driving force are provided for driving tools such as pin tackers that are mainly used for joining wood and gypsum boards. Has been. In the latter case, an electric motor is used as a drive source that uses an electric motor to move a striking driver back to a standby position against a spring driving force. Hereinafter, the former type of driving tool will be referred to as an electric driving tool, and the former compressed air drive type driving tool will be distinguished.

  A conventional technique related to such an electric driving tool is disclosed in Patent Document 1 below. In the following Patent Document 1, driving is performed by interposing a rack and pinion mechanism between a driving driver for driving the driving tool and a weight for reducing reaction, and moving the weight in the direction opposite to the driving direction at the time of driving. A technique for reducing the reaction of time is disclosed.

US Pat. No. 7,513,407

  However, according to the above-described conventional reaction reduction structure, although the hitting driver and the weight are synchronized via the rack and pinion mechanism, it is difficult to stop at the same time. As a result of the slight movement due to the inertial force, a large impact is applied to the meshing teeth of the rack gear and the pinion gear, and the durability of the rack and pinion mechanism may be impaired. In particular, in the case of the technique disclosed in Patent Document 1, since the bottom dead center damper of the hit driver is omitted, the hit driver moves down with inertial force after the weight is stopped at the top dead center. As a result, a large impact is applied to the meshing teeth of the rack and pinion mechanism.

  The present invention has been made to solve such a conventional problem, and in this type of driving tool, it is a mechanism for reducing an impact caused by a reaction at the time of driving, mainly for durability of the rack and pinion mechanism. The purpose is to increase.

  Said subject is solved by each following invention. According to a first aspect of the present invention, there is provided a striking driver that moves in a driving direction to hit a driving tool, a weight that moves in a direction opposite to the striking driver, and a weight and a striking driver interposed between the weight and the striking driver. It is a driving tool provided with a rack and pinion mechanism that moves them in directions opposite to each other. In the first invention, the rack and pinion mechanism includes a driving side rack gear on the impact driver side, a driven side rack gear on the weight side, a driving side pinion gear meshed with the driving side rack gear, and a driven side meshed with the driven side rack gear. It has a pinion gear. The driving side pinion gear and the driven side pinion gear are supported coaxially with each other and relatively rotatable within a certain angular range. Between the driving side pinion gear and the driven side pinion gear, an elastic member that elastically absorbs the relative rotation of both is interposed.

  According to the first aspect of the invention, the impact driver and the weight move in the opposite directions, and basically when one moves, the other moves in the opposite direction. However, it is also assumed that one of the impact driver and the weight reaches the moving end first and stops, and then the other moves by inertial force and reaches the moving end. Even in such a case, the drive side pinion gear and the driven side pinion gear are allowed to move in the other direction after the one reaches the moving end by deforming and relatively rotating the elastic member interposed therebetween, Thereby, the impact in the meshing direction applied mainly to the meshing teeth of the rack and pinion mechanism is elastically absorbed, and the durability of the rack and pinion mechanism can be enhanced.

  A second invention is a driving tool according to the first invention, wherein the rotational power is transmitted from the driving side pinion gear to the driven side pinion gear via the elastic member.

  According to the second invention, in the pinion gear, rotational power is transmitted between the two while the relative rotation between the driving side pinion gear and the driven side pinion gear is allowed.

  According to a third aspect of the present invention, there is provided a hit driver that moves in the driving direction and hits the driving tool, a weight that moves in the direction opposite to the hit driver, and the weight and the hit driver. It is a driving tool provided with a rack and pinion mechanism that moves them in directions opposite to each other. In the third aspect of the invention, after the impact driver reaches the moving end in the driving direction and stops, the moving operation of the weight to the moving end in the counter driving direction is allowed.

  According to the third aspect of the present invention, the striking driver and the weight are basically moved in opposite directions via the rack and pinion mechanism. However, according to the third aspect of the present invention, the weight driver is allowed to move to the moving end in the counter driving direction after the hit driver reaches the moving end in the driving direction and stops. For this reason, even if the weight driver moves to the moving end in the counter driving direction after the hitting driver reaches the moving end in the driving direction, an excessive external force is not applied to the rack and pinion mechanism. Can be increased.

  In a fourth aspect based on the third aspect, the rack and pinion mechanism includes a driving side rack gear on the impact driver side, a driven side rack gear on the weight side, a driving side pinion gear meshed with the driving side rack gear, and a driven side rack gear. And a driven pinion gear meshed with each other. In the third aspect of the invention, the backlash that satisfies the following condition is set for at least one of the driving side rack gear and the driving side pinion gear or the driven side rack gear and the driven side pinion gear. This backlash is caused by the movement of the weight in the counter driving direction while the weight is moved in the counter driving direction after the impact driver has stopped at the driving end in the driving direction and the meshing is shifted between the adjacent meshing teeth. The backlash (gap between the meshing teeth) is set to a size large enough to allow it to reach.

  According to the fourth invention, due to the backlash between the driving side rack gear and the driving side pinion gear or the backlash between the driven side rack gear and the driven side pinion gear, the movement operation of the weight alone by the inertial force after stopping the impact driver Is not allowed and an excessive external force is not applied to the rack and pinion, thereby improving the durability. The drive-side pinion gear and the driven-side pinion gear may be a single pinion gear integrated with each other in addition to a configuration that is coaxial with each other and relatively rotatable within a certain angular range.

  According to a fifth aspect of the present invention, there is provided a hit driver that moves in the driving direction and hits the driving tool, a weight that moves in a direction opposite to the hit driver, and the weight and the hit driver. It is a driving tool provided with a rack and pinion mechanism that moves them in directions opposite to each other. In the fifth aspect of the present invention, there is provided a moving end damper for restricting the moving end of the weight in the counter driving direction, and an auxiliary damper for providing elastic resistance with respect to the moving operation of the weight is interposed in front of the moving end damper. It has become.

  According to the fifth aspect of the present invention, elastic resistance (elastic movement resistance) is applied in two stages with respect to the movement operation of the weight in the anti-drive-in direction, and the inertial force is absorbed, whereby the rack and pinion mechanism is absorbed. The durability can be enhanced by preventing excessive external force from being applied.

  A sixth invention is a driving tool according to the fifth invention, wherein an elastic rubber body is used as the moving end damper and a leaf spring is used as the auxiliary damper.

  According to the sixth invention, in the process in which the weight moves in the counter driving direction, the leaf spring as the auxiliary damper interferes to give the weight an elastic movement resistance and reduce its inertial force. The weight comes into contact with the elastic rubber body as the moving end damper, and the shock at the time of stopping is absorbed. In this way, the inertia force and impact at the moving end of the weight in the anti-driving direction are absorbed in two stages, so that excessive external force is not applied to the rack and pinion mechanism, thereby enhancing its durability. Can do.

  According to a seventh invention, in the fifth or sixth invention, the rack and pinion mechanism includes a driving side rack gear on the impact driver side, a driven side rack gear on the weight side, a driving side pinion gear meshed with the driving side rack gear, A driven pinion gear meshed with the driven rack gear is provided. In the seventh aspect of the present invention, the driven rack gear is disengaged from the driven pinion gear when the weight is moved in the counter driving direction and receives the elastic resistance of the auxiliary damper.

  According to the seventh aspect of the present invention, when the elastic resistance by the auxiliary damper is received in the process in which the weight moves in the counter driving direction, the driven rack gear is disengaged from the driven pinion gear and the power transmission is interrupted. For this reason, even if the weight is moved to the moving end by inertia force alone after stopping the impact driver, the rack and pinion mechanism is not subjected to excessive external force, thereby increasing its durability. Can do. The drive-side pinion gear and the driven-side pinion gear may be a single pinion gear integrated with each other in addition to a configuration that is coaxial with each other and relatively rotatable within a certain angular range.

  An eighth invention is a driving tool according to any one of the first to seventh inventions, wherein the moving distance of the impact driver and the moving distance of the weight, which are made by the rack and pinion mechanism, are different from each other.

  According to the eighth aspect, the degree of freedom of arrangement of the impact driver and the weight is increased, and the driving tool can be configured in a compact manner.

  According to a ninth invention, in the eighth invention, in the rack and pinion mechanism, the number of teeth of the driving side pinion gear meshing with the driving side rack gear on the impact driver side is larger than the number of teeth of the driven side pinion gear meshing with the driven side rack gear on the weight side. The driving tool is set to be large and the moving distance of the weight is set to be smaller than the moving distance of the impact driver.

  According to the ninth aspect of the invention, a mechanism for reducing a reaction at the time of driving can be configured in a compact manner while ensuring a necessary moving distance of the hit dry.

It is a whole side view of a driving tool concerning this embodiment. In this figure, the internal structure is shown. It is the top view which looked at the driving tool which concerns on this embodiment from the arrow (II) direction in FIG. It is a side view of a drive mechanism and a striking mechanism. It is a perspective view of a drive mechanism and a striking mechanism. It is a figure explaining operation | movement of a drive mechanism. This figure shows the initial state of the rack and pinion mechanism. In the initial state, the striking frame is in a state of being retracted to a position before the retreat end. This figure is a view taken in the direction of arrows (V)-(V) in FIG. 4 and shows the rack and pinion mechanism as viewed from below. It is a figure explaining operation | movement of a drive mechanism. This figure shows a state immediately before the striking frame reaches the retracted end position and the engagement state of the second drive gear with respect to the second engagement portion is released. It is a figure explaining operation | movement of a drive mechanism. This figure shows a stage in which the striking frame has reached the forward end position and the driving operation has been performed. It is a figure explaining operation | movement of a drive mechanism. This figure shows a stage where the first driving gear starts to engage with the first engaging portion of the striking frame after the striking frame reaches the forward end position. It is a figure explaining operation | movement of a drive mechanism. This figure shows a stage in the middle of the striking frame being retracted from the forward end position by the rotation of the first drive gear. It is a figure explaining operation | movement of a drive mechanism. This figure shows a stage in the middle of the retraction of the striking frame when the second drive gear is engaged with the second engaging portion of the striking frame and immediately before reaching the initial position. It is a side view of a drive mechanism and a striking mechanism. This figure has shown the state in the middle of the downward motion of the impact driver. FIG. 12 is an enlarged view of the (XII) portion of FIG. 11, and is a side view showing a state in which the pinion gear is engaged with the drive-side rack gear. FIG. 12 is an enlarged view of the (XIII) part of FIG. 11, and is a side view showing a state in which the pinion gear is engaged with the driven rack gear. It is a side view of a drive mechanism and a striking mechanism. This figure shows a state immediately after the impact driver reaches the lower moving end and immediately before the weight reaches the upper moving end. It is the (XV) part enlarged view of FIG. 14, Comprising: It is a side view which shows the meshing state of the pinion gear with respect to a driven side rack gear. It is a side view which shows the meshing state of the pinion gear with respect to a driven side rack gear in the stage where the weight reached the upper moving end. FIG. 6 is a side view showing a state in which the pinion gear is engaged with the drive-side rack gear when the weight reaches the upper moving end. It is a disassembled perspective view of a pinion gear. It is a side view of the striking mechanism concerning a 2nd embodiment. This figure shows a state in which the weight is moving upward. It is a side view of the striking mechanism concerning a 2nd embodiment. This figure shows a stage where the weight comes into contact with the auxiliary damper. It is a side view of the striking mechanism concerning a 2nd embodiment. This figure shows a stage where the weight reaches the driving standby position. It is a side view of the striking mechanism concerning a 3rd embodiment. This figure shows a state immediately before the weight of the driven rack gear is disengaged from the pinion gear when the weight comes into contact with the auxiliary damper. It is a side view of the drive mechanism and impact mechanism concerning a 4th embodiment. It is a perspective view of the pinion gear which concerns on 4th Embodiment. It is a disassembled perspective view of the pinion gear which concerns on 4th Embodiment.

  Next, an embodiment of the present invention will be described with reference to FIGS. As shown in FIG. 1, the driving tool 1 according to the present embodiment includes a tool main body 10, a motor housing 20 that includes an electric motor 21 as a drive source, a grip 30 that is gripped by a user, A magazine 40 for loading a driving tool and a power supply unit 50 are provided. The tool main body 10 has a configuration in which a drive mechanism 60 and a striking mechanism 70 are housed in the main body housing 11. In the following description, the driving direction of the driving tool is the front side, the counter driving direction is the rear side, and the left and right directions are used with reference to the user. Accordingly, when the impact driver 3 moves forward, the impact tool T is impacted and is directly driven into the workpiece W.

  A driving nose portion 2 is provided in the front portion of the tool main body portion 10. When the driving driver 3 for driving the driving tool advances in the driving passage of the driving nose portion 2, the driving tool T is hit and driven from the injection port 4 at the tip thereof. The driving nose portion 2 is provided so as to be displaceable within a certain range in the front-rear direction (the driving direction) with respect to the tool main body portion 10. The driving operation is performed only when the injection port 4 is pressed against the workpiece W and the driving nose portion 2 is relatively retracted. For this reason, the single driving tool T driven out from the injection port 4 is driven into the workpiece W as it is. The backward movement of the driving nose portion 2 is detected by a nose sensor that is not visible in the drawing.

  The electric motor 21 can be activated by pulling a trigger switch lever 31 provided on the upper front surface of the grip portion 30 with a fingertip in a state where the driving nose portion 2 is moved backward. The impact driver 3 is returned to the retracted end position by the drive mechanism 60 using the electric motor 21 as a drive source. A main switch 32 is provided behind the switch lever 31. By pulling the switch lever 31, the main switch 32 is turned on and the electric motor 21 is started. When the pulling operation of the switch lever 31 is released, the main switch 32 is turned off and the electric motor 21 is stopped. Further, the electric motor 21 is automatically stopped after a predetermined time if an ON signal of a backward end sensor 18 described later is output even when the switch lever 31 is pulled.

  A main frame 12 is fixed in the main body housing 11. The main frame 12 is provided with a striking frame 13 and a weight base 14 movably back and forth independently. Between the front part and the rear part of the main frame 12, a round bar-shaped support shaft part 12a is suspended. The striking frame 13 is supported through the support shaft portion 12a so as to be movable in the front-rear direction. The rear part of the impact driver 3 is coupled to the upper part of the impact frame 13. A striking spring 17 is interposed between the rear portion of the striking frame 13 and the rear portion of the main frame 12 and around the support shaft portion 12a. The striking frame 13 is urged by the striking spring 17 in the forward direction (driving direction). The biasing force of the striking spring 17 becomes the striking force of the striking driver 3 and the driving force of the driving tool T. For this reason, a compression coil spring having a relatively large wire diameter and winding diameter is used for the impact spring 17.

  A pair of left and right rack and pinion mechanisms 80 are interposed between the striking frame 13 and the weight base 14. The striking frame 13 and the weight base 14 are displaced in directions opposite to each other via the rack and pinion mechanism 80. A driving mechanism 60 and a striking mechanism 70 are provided on the striking frame 13. The rack and pinion mechanism 80 will be described later.

  As shown in FIG. 1, the drive mechanism 60 includes a first drive gear 61 and a second drive gear 62 that are spur gears. The first drive gear 61 and the second drive gear 62 are rotatably supported on the lower part of the main body housing 11 via support shafts 61b and 62c, respectively. The rotational output of the electric motor 21 is decelerated and output to the output gear 21a. The output gear 21 a is meshed with the first drive gear 61. The first drive gear 61 is engaged with the second drive gear 62. For this reason, when the electric motor 21 is started, the first drive gear 61 rotates and the second drive gear 62 rotates in the opposite direction to the first drive gear 61.

  A first engagement roller 61 a is rotatably supported on the upper surface of the first drive gear 61. A second engagement roller 62 a is rotatably supported on the upper surface of the second drive gear 62. Further, an auxiliary engagement portion 62b is provided on the upper surface of the second drive gear 62 adjacent to the second engagement roller 62a. The first engagement roller 61a and the second engagement roller 62a have the same diameter, but the first engagement roller 61a is set to be taller (longer in the axial direction) than the second engagement roller 62a. Yes. The auxiliary engagement part 62b has the same height as the second engagement roller 62a.

  As shown in FIGS. 5 to 10, the lower surface of the striking frame 13 is provided with a first engagement portion 15 and a second engagement portion 16 projecting downward at a predetermined interval in the front-rear direction. Yes. The first engagement portion 15 is disposed in a substantially half area on the left side of the striking frame 13, and the second engagement portion 16 is disposed in a substantially half area on the right side. Both engaging portions 15 and 16 are arranged in parallel to each other. As shown in FIG. 1, the downward projecting dimensions of the first engaging portion 15 and the second engaging portion 16 are different. The overhanging dimension of the first engaging part 15 is small, and the overhanging dimension of the second engaging part 16 is set large. For this reason, although the high 1st engagement roller 61a is engaged with the 1st engagement part 15, the low 2nd engagement roller 62a is not engaged. The second engagement roller 62a is engaged only with the second engagement portion 16 that protrudes greatly downward.

  In the initial state shown in FIG. 5, the driving nose portion 2 is pressed against the driven material W to be relatively retracted, and the electric motor 21 is started by pulling the switch lever 31 in the retracted state. When the first driving gear 61 and the second driving gear 62 are rotated by the activation of the electric motor 21, the striking frame 13 is retracted from the initial position and a driving operation is performed. After the driving, the electric motor 21 continues to start for a certain time, so that the striking frame 13 is returned to the initial position shown in FIG. Details of the movement operation of the striking frame 13 accompanying one driving operation are shown in FIGS. First, FIG. 5 shows an initial state in which the striking frame 13 is located in front of the retracted end (initial position). In this initial state, the impact driver 3 is located slightly in front of the backward end.

  In the initial state shown in FIG. 5, the second engagement roller 62 a is in contact with the front surface side of the second engagement portion 16. For this reason, when the electric motor 21 is activated and the first drive gear 61 rotates counterclockwise and the second drive gear 62 rotates clockwise, the striking frame 13 is further retracted. FIG. 6 shows a state immediately before the hitting frame 13 reaches the retracted end position. The state immediately before the retracted end shown in FIG. 6 is a state immediately before the auxiliary engagement portion 62 b is disengaged from the second engagement portion 16. When the striking frame 13 reaches the retracted end position through the state immediately before the retracted end shown in FIG. 6, the auxiliary engaging portion 62 b is disengaged from the second engaging portion 16. At the moment when the auxiliary engaging portion 62b is disengaged from the second engaging portion 16, the striking frame 13 moves forward by the urging force of the striking spring 17, so that the striking driver 3 moves forward in the driving passage of the driving nose portion 2. In the process of moving forward in the driving path, a single driving tool T is hit by the hitting driver 3 and is driven into the workpiece W as it is.

  A forward end damper 19 is attached to the front portion of the main frame 12. Therefore, as shown in FIG. 7, the striking frame 13 contacts the forward end damper 19 and reaches the forward end position. The striking frame 13 is stopped at the forward end position by coming into contact with the forward end damper 19, and the impact at the time of contact is absorbed by the forward end damper 19 being elastically deformed.

  As shown in FIG. 1, the retracted end position of the striking frame 13 is detected by the retracted end sensor 18 described above. When it is detected by the backward end sensor 18 that the strike frame 13 has reached the backward end position, the electric motor 21 is stopped after a predetermined time based on the output signal, and the strike frame 13 is initially shown in FIG. Return to position. The electric motor 21 is in the activated state at the driving stage in which the striking frame 13 moves forward by the urging force of the striking spring 17, but the first and second engaging rollers 61a and 62a and the auxiliary engaging portion 62b are as shown in FIG. Since both are disengaged from the first and second engaging portions 15 and 16, the rotational power of the electric motor 21 is separated from the striking frame 13 side. For this reason, the hitting driver 3 hits the driving tool T with a sufficient hitting force by the biasing force of the hitting spring 17 without receiving the power on the drive mechanism 60 side as resistance.

  After the driving tool T is struck, the start-up state of the electric motor 21 is continuously maintained, whereby the first drive gear 61 rotates counterclockwise as shown in FIG. 8 and the first engagement roller 61a is in the first engagement state. It contacts the front surface of the joint portion 15. As the first drive gear 61 further rotates counterclockwise as shown in FIG. 9 in this abutting state, the striking frame 13 begins to retreat against the striking spring 17. When the first drive gear 61 further rotates counterclockwise while retracting the striking frame 13, the first engagement roller 61a is disengaged from the first engagement portion 15 as shown in FIG. 62 a is engaged with the front surface of the second engaging portion 16. For this reason, the first drive gear 61 rotates in the counterclockwise direction as it is, and accordingly, the second drive gear 62 rotates in the clockwise direction indicated by the arrow in the drawing, so that the second engagement portion 16 is in the second engagement. The roller 62 a is pushed backward, whereby the striking frame 13 is further retracted against the striking spring 17.

  As described above, the retraction operation of the striking frame 13 is continued from the first engagement roller 61a of the first drive gear 61 to the second engagement roller 62a of the second drive gear 62, whereby the striking frame 13 is moved. It can be moved backward with a large stroke. As shown in FIG. 10, the first driving gear 61 and the second driving gear 62 continue to rotate in the direction of the arrow, whereby the second engaging portion 16 is pushed by the second engaging roller 62a. It further retreats against the impact spring 17 and returns to the initial position shown in FIG. 5, and at this stage, the electric motor 21 is automatically stopped.

  Further, the reaction at the time of striking and driving when the striking driver 3 moves forward is absorbed by the pair of left and right weights 5 moving in the direction opposite to the driving direction. As shown in FIGS. 3 and 4, the pair of left and right weights 5 are supported by the weight base 14 described above. The weight base 14 is supported so as to be movable back and forth with respect to the main frame 12. Cylindrical weights 5 are attached to the upper surfaces of the left and right side portions of the weight base 14, respectively. Return springs 6 are interposed between the weights 5 and the front portion of the main frame 12, respectively. Both return weights 5 are urged by the return spring 6 in the backward direction. In this respect, the urging direction is opposite to the striking spring 17 that urges the striking frame 13 in the forward direction.

  A backward end damper 7 having a cylindrical body shape with substantially the same diameter is attached to the rear surfaces of both weights 5. The retractable end damper 7 is made of rubber and has appropriate elasticity. When both the back end dampers 7 are brought into contact with the rear surface of the main frame 12, the back end position of the weight 5 is regulated, and the impact when the back end position is reached by the biasing force of the return spring 6 is absorbed. The

  The moving direction of the left and right weights 5 and the moving direction of the impact driver 3 are opposite to each other and are synchronized. Thereby, the reaction added to the driving tool 1 generated by driving the driving tool T to the driven material W by the driving driver 3 is absorbed. In order to make the moving direction of the left and right weights 5 and the moving direction of the batting driver 3 opposite to each other and synchronized, a pair of left and right racks are placed between the weight base 14 and the batting frame 13. A pinion mechanism 80 is interposed. The left and right rack and pinion mechanisms 80 have the same configuration. Hereinafter, the right rack and pinion mechanism 80 shown in the figure will be described.

  The rack and pinion mechanism 80 includes a driving side rack gear 81, a driven side rack gear 82, a driving side pinion gear 83 meshed with the driving side rack gear 81, and a driven side pinion gear 86 meshed with the driven side rack gear 82. The drive side rack gear 81 is attached along the side portion of the striking frame 13. The driven rack gear 82 is coupled to the side portion of the weight base 14. For this reason, the driving side rack gear 81 is arranged to be movable back and forth along the lower part of the main frame 12, and the driven side rack gear 82 is arranged to be movable back and forth along the upper part of the main frame 12. The lower drive-side rack gear 81 is mounted with the meshing teeth facing upward, and the upper driven rack gear 82 is mounted with the meshing teeth facing downward. Further, the driving side rack gear 81 and the driven side rack gear 82 are arranged so as to be shifted from each other to the left and right. The driving-side pinion gear 83 and the driven-side pinion gear 86 are supported on the side of the main frame 12 via the support shaft 85 so as to be relatively rotatable relative to each other. The driving side pinion gear 83 and the driven side pinion gear 86 are supported so as to be rotatable relative to each other within a certain angular range.

  In the rack and pinion mechanism 80, the drive side rack gear 81 and the driven side rack gear 82 are indirectly meshed with each other via the drive side pinion gear 83 and the driven side pinion gear 86, so that the main frame 12 and the weight base 14 are in opposite directions. Move in sync with. For this reason, when the striking frame 13 is retracted against the striking spring 17 from the forward end position shown in FIG. 7 to the backward end position immediately after that shown in FIG. It moves forward against the return spring 6 from the position abutting against the damper 7 toward the forward end position. At the stage where the striking frame 13 moves forward from the retracted end position immediately after that shown in FIG. 10, the weight 5 moves backward from the advanced end position by the biasing force of the return spring 6.

  In this embodiment, the timing at which the striking frame 13 contacts the forward end damper 19 and reaches the forward end position is slightly different from the timing at which the weight 5 contacts the backward end damper 7 and reaches the backward end position. Thus, when the striking frame 13 reaches the forward end position first and then the weight 5 reaches the backward end position after a short time, only the weight 5 moves, so that the rack and pinion mechanism 80 has a special meshing tooth. A device has been devised to prevent excessive external force from being applied.

  FIG. 11 shows the state of the rack and pinion mechanism 80 and other parts immediately before the hitting frame 13 reaches the forward end position. At this stage, there is a gap between the front end of the striking frame 13 and the forward end damper 19. Further, a gap larger than this is vacant between the rear end damper 7 and the rear portion of the main frame 12. At this stage, the meshing state of the meshing teeth of the driving side pinion gear 83 with the driving side rack gear 81 is shown in FIG. 12, and the meshing state of the meshing teeth of the driven side pinion gear 86 with the driven side rack gear 82 is shown in FIG.

  As shown in FIG. 12, the meshing teeth 81a of the drive-side rack gear 81 abuts (meshes) with the meshing teeth 83a of the drive-side pinion gear 83, and the drive-side rack gear 81 advances in the direction of arrow F in this abutting state. As a result, the drive-side pinion gear 83 rotates in the direction of arrow C. A gap 80a is generated between the meshing tooth 81a of the drive side rack gear 81 and the meshing tooth 83a of the drive side pinion gear 83 located on the rear side. For this reason, backlash (shaking in the meshing direction, the same applies hereinafter) corresponding to the gap 80a occurs between the drive-side rack gear 81 and the drive-side pinion gear 83.

  As shown in FIG. 13, the meshing tooth 86a of the driven pinion gear 86 is in contact with the front surface of the meshing tooth 82a of the driven rack gear 82, and the driven pinion gear 86 rotates in the direction of arrow C in this contact state. The side rack gear 82 is pushed in the backward direction and retracts in the arrow R direction. The driven rack gear 82 moves backward. A gap 80b is generated between the meshing tooth 86a of the driven pinion gear 86 and the meshing tooth 82a of the driven rack gear 82 located on the front side thereof. For this reason, a backlash corresponding to the gap 80 b occurs between the driven pinion gear 86 and the driven rack gear 82.

  As shown in FIG. 14, the striking frame 13 is further advanced and comes into contact with the forward end damper 19 to stop the forward movement. When the striking frame 13 comes into contact with the forward end damper 19 and stops, the weight 5 does not reach the backward end, and a slight gap (idle distance 7a) is formed between the rear portion of the main frame 12 and the backward end damper 7. Is left.

  For this reason, when the striking frame 13 reaches the forward end position (initial position), the weight 5 is further retracted by the idle travel distance 7 a mainly by the biasing force of the return spring 6. At this stage, the drive side rack gear 81 and the drive side pinion gear 83 do not move while maintaining the meshing state shown in FIG. At this stage, only the driven rack gear 82 moves backward with respect to the driven pinion gear 86. For this reason, through the state shown in FIG. 15 from the meshing state shown in FIG. 13, the meshing tooth 82a of the driven rack gear 82 is separated from the meshing tooth 86a that has been in contact at the stage shown in FIG. In this state, the lever contacts the meshing teeth 86a on the front side in the rotational direction.

  The meshing tooth 82a of the driven side rack gear 82 is brought into contact with the meshing tooth 86a of the driven side pinion gear 86 from the front side, and the driven side rack gear 82 is further retracted in the direction of the arrow R to push the meshing tooth 86a backward. Then, the driven side pinion gear 86 slightly rotates again in the direction of arrow C. When the driven pinion gear 86 is pushed in the direction of arrow C and slightly rotates, the meshing state of the drive side pinion gear 83 with the drive side rack gear 81 is displaced from the state shown in FIG. 12 to the state shown in FIG. In the state shown in FIG. 17, the meshing teeth 83a of the drive-side pinion gear 83 are slightly displaced forward and are positioned between the adjacent meshing teeth 81a of the drive-side rack gear 81 adjacent to each other. It is not in contact. The idling of the drive-side pinion gear 83 in the direction of arrow C (displacement to the front side of the meshing teeth 83a) at this stage is set within a range that cancels backlash 80a at the stage shown in FIG.

  Thus, in this embodiment, the meshing tooth 82a of the driven rack gear 82 is displaced in the backward direction with respect to the meshing tooth 86a of the driven pinion gear 86 (i.e., idle running) until it comes into contact with the meshing tooth 86a on the front side. (FIG. 13 → FIG. 15 → FIG. 16) In addition, the driven pinion gear 86 is pushed by the driven rack gear 82 and idles (FIG. 12 → FIG. 17) so that the weight 5 reaches the retracted end position. The backlash 80b between the teeth 82a and 86a is set to be large. In the present embodiment, the backlash 80a between the meshing teeth 81a of the driving side rack gear 81 and the meshing teeth 83a of the driving side pinion gear 83, and the space between the meshing teeth 82a of the driven side rack gear 82 and the meshing teeth 86a of the driven side pinion gear 86. The backlash 80b is set to be larger than a normal involute gear. In order to set the backlash 80a, 80b to be larger than that of a normal involute gear, each element such as a pressure angle, a pitch, and a module of the driving side rack gear 81, the driven side rack gear 82, the driving side and the driven side pinion gears 83, 86, etc. Is set appropriately. As a result, after the striking frame 13 reaches the forward end position (initial position) and the driving side rack gear 81 is stopped, the driving side and driven side pinion gears 83 and 86 are moved from FIG. 12 to FIG. 13 to FIG. 16 → FIG. 17, through the displacement (idle) in the direction of arrow C, the backward movement of the idle distance 7a of the weight 5 is absorbed, and the meshing teeth 81a and 82a of the rack and pinion mechanism 80 are absorbed. , 83a, 86a is not subjected to excessive external force.

  After the striking frame 13 reaches the forward end position and driving of the driving tool is completed, the weight 5 moves backward by a slight idling distance 7a to reach the backward end without applying an excessive external force to the rack and pinion mechanism 80. Since it is a structure, it can absorb more reliably the reaction at the time of driving added to the said driving tool 1, and this can improve the durability with respect to the reaction at the time of driving of the said driving tool 1, and workability | operativity. Can be increased.

  The driving tool 1 of the present embodiment is devised to more reliably absorb the reaction during driving. As shown in FIG. 18, a reaction absorption function is provided between the driving side pinion gear 83 and the driven side pinion gear 86. As described above, the drive side pinion gear 83 and the driven side pinion gear 86 are supported via the support shaft 85 so as to be relatively rotatable within a certain angular range. In the present embodiment, the drive side pinion gear 83 and the driven side pinion gear 86 have the same gear diameter and the same number of teeth. The drive side pinion gear 83 is meshed with the drive side rack gear 81. The driven side pinion gear 86 is meshed with the driven side rack gear 82. The drive-side pinion gear 83 and the driven-side pinion gear 86 are each provided with two arc-shaped holding holes 83b and 86b. In each of the drive-side pinion gear 83 and the driven-side pinion gear 86, the two holding holes 83b and 86b are disposed opposite to each other around the support holes 83c and 86c through which the support shaft 85 is inserted.

  A common support shaft 85 is inserted into the support holes 83c and 86c, and the drive side pinion gear 83 and the driven side pinion gear 86 are supported coaxially and relatively rotatable. A common elastic member 84 is inserted into each of the two holding holes 83 b and 86 b of the driving side pinion gear 83 and the driven side pinion gear 86. The two elastic members 84 are respectively inserted between the holding hole 83 b of the driving side pinion gear 83 and the holding hole 86 b of the driven side pinion gear 86. The two elastic members 84 are made of rubber and have moderate elasticity. The rubber elastic member 84 provides elasticity in the relative rotational direction between the driving side pinion gear 83 and the driven side pinion gear 86.

  By providing elastic performance in the relative rotational direction between the drive-side pinion gear 83 and the driven-side pinion gear 86, the drive-side rack gear 81 and the driven-side rack gear 82 whose movement operations are synchronized with each other in one stop state. The other movement is elastically allowed. According to the driving-side pinion gear 83 and the driven-side pinion gear 86, after stopping at the forward end position of the striking frame 13, the driving-side pinion gear 83 and the driven-side pinion gear 86 elastically deform the elastic member 84 to make a relative displacement in the rotational direction. By doing so, it is possible to secure a longer idle travel distance 7a of the weight 5 while avoiding excessive external force being applied to the rack and pinion mechanism 80, and more reliably absorb the reaction at the time of driving in this respect. can do.

  As shown in FIG. 1, the grip portion 30 extends downward from the lower surface of the rear portion of the tool body portion 10 with a length and thickness that are easy for a user to hold with one hand. A power supply unit 50 is provided below the grip unit 30. A flat battery mounting portion 51 is provided at the lower portion of the grip portion 30. The battery attachment portion 51 is provided in a state of protruding forward from the lower portion of the grip portion 30. The motor housing portion 20 is coupled to the upper surface of the front portion of the battery attachment portion 51.

  A battery pack 52 is attached to the lower surface of the battery attachment portion 51. Although not visible in the figure, a pair of left and right rail portions for mechanically connecting the battery pack 52 and a positive and negative terminal plate for electrical connection are disposed on the lower surface of the battery mounting portion 51. . The battery pack 52 is a lithium ion battery having an output voltage of 14.4 V, and is a slide-attached battery pack that can be removed by sliding backward with respect to the battery attachment portion 51 and can be attached by sliding forward. Yes. The battery pack 52 can be repeatedly used by removing it from the battery mounting portion 51 and charging it with a separately prepared charger. The battery pack 52 is a versatile battery pack that can be used as a power source for other electric tools such as a rechargeable screw tightener and a cutting tool.

  Inside the battery mounting portion 51, a controller 53 having a control circuit board for controlling the operation of the electric motor 21 and a power circuit board is housed. The battery attachment unit 51, the battery pack 52, and the controller 53 constitute a power supply unit 50. A U-shaped hook 54 is provided on the side of the battery mounting portion 51. By hooking the hook 54 on a work shelf or a stepladder, the driving tool 1 can be stored upside down while being turned upside down.

  The main body housing 11 of the tool body 10, the housing of the motor housing 20, the housing of the grip 30 and the housing of the battery mounting portion 51 are made of a resin left and right half housing formed by integrally molding the housings of each portion, and a plurality of fixing screws 25 have a left and right halved structure coupled to each other.

  The magazine 40 can be loaded with a plate-like connection driving tool in which a large number of driving tools T are temporarily fixed in parallel with each other. The loaded connection driving tool is driven in conjunction with the driving operation of the tool body 10. It has a function of feeding the driving tools T one by one into the driving path by pitch-feeding to the nose portion 2 side.

  According to the driving tool 1 of the present embodiment configured as described above, the impact applied mainly to the meshing teeth 81a, 82a, 83a, 86a of the rack and pinion mechanism 80 can be reduced and its durability can be increased. . In the present embodiment, an elastic member 84 that is elastically deformable in the rotational direction is interposed between the drive-side pinion gear 83 and the driven-side pinion gear 86 that are relatively rotatable within a certain angle range.

  According to such a configuration, for example, after the impact driver 3 reaches the forward end first and stops, even if the weight 5 moves backward by the inertia force and reaches the backward end position after a short time, the drive-side pinion gear 83 and the driven pinion gear 86 deform relative to each other by deforming the elastic member 84 interposed therebetween, so that the impact in the meshing direction added mainly to the meshing teeth 81a, 82a, 83a, 86a of the rack and pinion mechanism 80 Can be absorbed elastically and the impact resistance of the rack and pinion mechanism 80 can be enhanced.

  In addition, in this embodiment, the backlash between the driving side rack gear 81 and the driving side pinion gear 83 (the gap between the meshing teeth 81a and 83a) 80a and the backlash between the driven side rack gear 82 and the driven side pinion gear 86 are performed. The impact resistance of the rack and pinion mechanism 80 is also enhanced by appropriately setting (the gap between the meshing teeth 82a and 86a) 80b. The backlashes 80a and 80b are configured so that the weight 5 moves backward in the counter driving direction after the driving driver 3 reaches the moving end in the driving direction and stops (after the driving frame 13 comes into contact with the forward end damper 19 and stops). As a result, the backlash is large enough to allow the weight 5 to reach the retracted end position while the meshing between adjacent meshing teeth is shifted, and is relatively large compared to a normal involute gear. Is set to

  As described above, the backlashes 80a and 80b of the driving side rack gear 81 and the driven side rack gear 82 with respect to the driving side and driven side pinion gears 83 and 86 allow the single movement operation of the weight 5 by the inertial force after the impact driver 3 stops. As a result, no excessive external force is applied to the rack and pinion mechanism 80, and the durability thereof can be improved.

  FIGS. 19 to 21 show a striking mechanism 71 according to the second embodiment, which is devised for more reliably absorbing the impact caused by the movement of the weight 5 to the retracted end. The striking mechanism 71 of the second embodiment is different from the striking mechanism 70 of the first embodiment illustrated above in that it includes an auxiliary damper 8 for absorbing shock in the backward movement of the weight 5. The members and configurations that do not need to be changed are denoted by the same reference numerals and the description thereof is omitted.

  In the first embodiment described above, the backward end damper 7 is attached to the rear surface of the weight 5. In the second embodiment, as shown in FIG. 19, a retreat end damper 9 for restricting the retreat operation of the weight 26 is attached to the main frame 12 side. A pair of reverse end dampers 9 are provided on the left and right. In the second embodiment, one leaf spring (plate spring) is used as the auxiliary damper 8. The auxiliary damper 8 is disposed between the left and right receding end dampers 9 in the left-right direction position. The auxiliary damper 8 is disposed so as to stand upward from the bottom of the main frame 12 in front of the backward end damper 9 with respect to the position in the front-rear direction.

  As described above, the striking frame 13 moves forward by the urging force of the striking spring 17 through the stage shown in FIG. The rack and pinion mechanism 80 synchronizes the movement directions of the striking frame 13 and the weight 26 in opposite directions. Therefore, when the striking frame 13 moves forward, the weight 26 moves backward by the biasing force of the return spring 6. The weight 26 abuts on the auxiliary damper 8 as shown in FIG. 20 through the stage of retreating shown in FIG. 19, and then abuts on the retreat end damper 9 as shown in FIG.

  The receding operation of the weight 26 absorbs the recoil in the upward lifting direction received by the driving tool 1 during driving. As described above, the advancing end position of the striking frame 13 is regulated by contacting the advancing end damper 19, and the impact at the abutting is absorbed by the elastic deformation of the advancing end damper 19. On the other hand, the retracted end position of the weight 26 is regulated by contacting the retracted end damper 9, and the impact at the time of contact is absorbed by the elastic deformation of the retracted end damper 9. Moreover, immediately before the weight 26 comes into contact with the backward end damper 9, the inertial force accompanying the backward movement of the weight 26 is absorbed by the auxiliary damper 8.

  Thus, the inertia force and the urging force of the return spring 6 during the backward movement of the weight 26 are absorbed by the auxiliary damper 8, and the backward movement of the weight 26 is decelerated. In this decelerated state, the weight 26 is brought into contact with the backward end damper 9. . The inertia force during the backward movement of the weight 26 and the urging force of the return spring 6 are absorbed in two stages by the auxiliary damper 8 and the backward end damper 9, so that the shock applied to the rack and pinion mechanism 80 can be more reliably performed. It can be reduced to increase its durability.

  FIG. 22 shows a striking mechanism 71 according to the third embodiment. The third embodiment has a configuration obtained by further modifying the second embodiment, and a missing tooth portion 82b in which the meshing teeth 82a are missing is provided on the front side of the driven side rack gear 82 (the rack is short). ) The range of the missing tooth portion 82b is set to a range in which the engagement with the driven-side pinion gear 86 is released after contacting the auxiliary damper 8 during the backward movement of the weight 26 as shown in the figure. In the third embodiment, the right five meshing teeth 82a in the second embodiment are omitted to form a missing tooth portion 82b.

  According to the missing tooth portion 82b, after the weight 26 comes into contact with the auxiliary damper 8, the engagement of the driven rack gear 82 with the driven pinion gear 86 is disengaged (the power transmission path is interrupted). During the movement to the retracted end position by force, an excessive external force is not added to the driven pinion gear 86, and hence the driving side pinion gear 83 and the driving side rack gear 81, and in this respect, the durability of the rack and pinion mechanism 80 is improved. Can be increased more reliably.

  In the case of the third embodiment, the elastic force of the auxiliary damper 8 is set to a biasing force larger than the spring biasing force of the return spring 6. Therefore, after the weight 5 reaches the retracted end position due to the biasing force of the return spring 6 and the large inertial force and the inertial force is completely absorbed, the weight 26 is moved to the position shown in FIG. 22 by the biasing force of the auxiliary damper 8. Returned. When the weight 26 is returned to the position shown in FIG. 22 by the urging force of the auxiliary damper 8, the meshing teeth 82 a at the front end of the driven rack gear 82 are engaged with the driven pinion gear 86. Therefore, after that, the electric motor 21 is started and the drive side rack gear 81 starts to move backward. As a result, when the drive side and driven side pinion gears 83 and 86 rotate in the clockwise direction in the figure, the meshing teeth 82a of the driven side rack gear 82 and the driven side are driven. The forward movement is started by the meshing state of the meshing teeth 86a of the side pinion gear 86. For this reason, the malfunction on operation resulting from providing the missing tooth part 82b in the driven side rack gear 82 does not occur.

  According to the second embodiment exemplified above, the inertia force is absorbed in two steps of the auxiliary damper 8 as the auxiliary damper and the reverse end damper 9 in the backward movement of the weight 5. As a result, the durability can be enhanced by preventing an excessive external force from being applied to the rack and pinion mechanism 80 more reliably.

  By using a leaf spring that is elastically displaced with a relatively large amplitude as the auxiliary damper 8, the inertia force of the weight 26 during the backward movement can be more reliably absorbed and decelerated. In this respect, the rack and pinion mechanism 80 Therefore, it is possible to prevent an excessive external force from being applied.

  Further, according to the driving tool 1 of the third embodiment, when the weight 26 is retracted in the counter driving direction, the driven rack gear 82 meshes with the driven pinion gear 86 when the auxiliary damper 8 receives the elastic resistance. It is configured to come off. Therefore, the power transmission path between the driven-side pinion gear 86 and the driven-side rack gear 82 is separated while the weight 26 is moved back to the retracted end by the inertial force and the biasing force of the return spring 6. An excessive external force is not applied to the meshing teeth 86a of the side pinion gear 86 and the meshing teeth 83a of the driving side pinion gear 83 and the meshing teeth 81a of the driving side rack gear 81, thereby ensuring the durability of the rack and pinion mechanism 80 more reliably. Can be increased.

  The embodiment described above can be further modified. For example, in the rack and pinion mechanism 80, the configuration in which the power of the driving side rack gear 81 is transmitted to the driven side rack gear 82 by the two pinion gears of the driving side pinion gear 83 and the driven side pinion gear 86 is illustrated. It is good also as a structure which uses an integrated pinion gear. Even when such an integrated pinion gear is used, the same operational effects can be obtained by setting the backlashes 80a and 80b exemplified between the driving side rack gear and the driven side rack gear.

  In addition, although the drive side pinion gear 83 and the driven side pinion gear 86 have been exemplified to have the same diameter (gear diameter) and the same number of teeth, the impact driver 3 can have a different gear diameter and number of teeth. The stroke of the weight 5 and the stroke of the weight 5 (26) can be different from each other. By reducing the gear diameter or the number of teeth of the driven pinion gear 86 with respect to the drive side pinion gear 83, the stroke of the weight 5 (26) can be made smaller (decelerated) than the stroke of the impact driver 3. The resistance to the downsizing and the impact driver 3 can be reduced. Conversely, by increasing the gear diameter or the number of teeth of the driven-side pinion gear 86 as compared with the driving-side pinion gear 83, the stroke of the weight 5 (26) can be made larger (accelerated) than the stroke of the impact driver 3, Thereby, the shock absorption capacity of the weight 5 (26) can be enhanced.

  FIG. 23 shows a rack and pinion mechanism 90 according to a fourth embodiment provided with a drive-side pinion gear and a driven-side pinion gear having different gear diameters and number of teeth. The rack and pinion mechanism 90 according to the fourth embodiment includes a pinion gear 96 in which the number of teeth of the driving side pinion gear 93 is set larger than the number of teeth of the driven side pinion gear 94. In addition, about the member and structure which do not require a change, the description is abbreviate | omitted using a same code | symbol.

  Further, in the fourth embodiment, the driving side rack gear 91 is arranged along the upper side of the main frame 12, and the driven side rack gear 92 is arranged along the lower side, which is upside down from the first to third embodiments. It has become. For this reason, in the striking mechanism 74 of the fourth embodiment shown in FIG. 23, the weight 5 and the return spring 6 are disposed below the pinion gear 96. Hereinafter, apart from the pinion gear 96 to be described, the left and right weights 5 are arranged below the main frame 12 so that the left and right overhangs are shifted downward. As a result, the tool body 10 is mainly reduced in the width direction. be able to.

  As shown in FIGS. 23 to 25, the pinion gear 96 according to the fourth embodiment has a configuration in which a driving side pinion gear 93 and a driven side pinion gear 94 are coaxially coupled via a plurality of elastic members 95. A spur gear with 15 teeth is used for the drive-side pinion gear 93, and a spur gear with 12 teeth is used for the driven-side pinion gear 94. The drive side pinion gear 93 is meshed with the drive side rack gear 91. The drive side rack gear 91 is coupled along the left and right side portions of the striking frame 13. The driven side pinion gear 94 is meshed with the driven side rack gear 92. A pair of left and right driven rack gears 92 are coupled along the left and right side portions of the weight base 14. A cylindrical weight 5 is coupled to the lower surfaces of the left and right side portions of the weight base 14. Return springs 6 are interposed between the left and right weights 5 and the front portion of the main frame 12, respectively. This is the same as in the first to third embodiments.

  The drive-side pinion gear 93 with 15 teeth and the driven-side pinion gear 94 with 12 teeth constitute a pinion gear 96 with a reduction ratio of 1.25. For this reason, the moving distance (stroke) of the driven rack gear 92 is set to 80% of the moving distance (stroke) of the driving rack gear 91. Also in the fourth embodiment, the backlash (gap 80a) of the driving side pinion gear 93 with respect to the driving side rack gear 91 and the backlash (gap 80b) of the driven side pinion gear 94 with respect to the driven side rack gear 92 are described in the first to third embodiments. It is set appropriately as well.

  As shown in FIG. 25, in the pinion gear 96 according to the fourth embodiment, four cylindrical rubber pins are used as the elastic member 95. The drive-side pinion gear 93 is provided with two arc-shaped holding holes 93a facing each other around a central support hole 93b. The driven-side pinion gear 94 is integrally provided with two engaging portions 94a projecting in a circular arc shape around the central support hole 94b. In the coupled state of the driving side pinion gear 93 and the driven side pinion gear 94, the two engaging portions 94a respectively enter the holding holes 93a. One elastic member 95 is sandwiched between both ends of the engaging portion 94a and both ends of the holding hole 93a.

  The driving-side pinion gear 93 and the driven-side pinion gear 94 are relatively rotatable within a range in which the total four elastic members 95 are elastically deformed and the engaging portion 94a can be displaced in the circumferential direction in the holding hole 93a. By elastically deforming the four elastic members 95 and causing the drive side pinion gear 93 and the driven side pinion gear 94 to rotate relative to each other, the movement operation of the drive side rack gear 91 and the driven side rack gear 92 in one stop state is elastically performed. Permissible. After stopping the drive-side rack gear 91 by driving, the idle running distance 7a of the weight 5 is secured, so that the reaction at the time of driving is absorbed. This point is the same as the pinion gear of the rack and pinion mechanism 80 according to the first to third embodiments.

  According to the pinion gear 96 of the fourth embodiment configured as described above, the number of teeth (15) of the driving side pinion gear 93 is set larger than the number of teeth (12) of the driven side pinion gear 94, and the moving distance of the weight 5 is increased. Is set smaller than the moving distance of the impact driver 3. Since the moving distance of the weight 5 can be reduced while ensuring the equivalent shock absorption capability, the degree of freedom of the arrangement can be increased and the tool body 10 can be made compact.

  The fourth embodiment described above exemplifies a configuration in which the number of teeth of the drive-side pinion gear 93 is made larger than the number of teeth of the driven-side pinion gear 94 and the moving distance of the drive-side rack gear 91 is reduced and transmitted to the driven-side rack gear 92. However, conversely, the number of teeth of the drive-side pinion gear may be made smaller than the number of teeth of the driven-side pinion gear so that the movement distance of the driven-side rack gear becomes larger (speed increase) than the movement distance of the drive-side rack gear.

  In addition, in order to give the rack and pinion mechanism the above-described speed change function, the number of teeth of the driving side pinion gear and the driven side pinion gear is made different from each other, and the gear diameter or the module is made different from each other. Can also have the same speed change function.

  The variable speed pinion gears with different gear diameters and number of teeth on the drive side and driven side are integrated on the drive side and driven side in addition to the configuration where the drive side and driven side are individual pinion gears as illustrated. The present invention can also be applied to a pinion gear made.

  In the first to fourth embodiments, in the driving mechanism 60, the configuration in which the striking frame 13 is largely retracted in two stages by the first driving gear 61 and the second driving gear 62 is exemplified. It is possible to reduce the size of the driving tool as a configuration in which the frame is retracted by a smaller distance than illustrated.

  Moreover, although the direct current power source type driving tool 1 using the battery pack 52 as a power source is illustrated, the present invention can be similarly applied to a driving tool using a commercial AC power source such as 100V as a power source.

T ... Driving tool W ... Placing material 1 ... Driving tool (rechargeable pin tacker)
2 ... Driving nose part 3 ... Blow driver 4 ... Injection port 5 ... Weight (first embodiment)
6 ... Return spring 7 ... Back end damper (first embodiment)
7a: Clearance (idle distance)
8 ... Auxiliary damper (leaf spring)
9: Back end damper (second and third embodiments)
DESCRIPTION OF SYMBOLS 10 ... Tool body part 11 ... Main body housing 12 ... Main frame, 12a ... Supporting shaft part 13 ... Impacting frame 14 ... Weight base 15 ... 1st engaging part 16 ... 2nd engaging part 17 ... Impacting spring 18 ... Back end sensor DESCRIPTION OF SYMBOLS 19 ... Advance end damper 20 ... Motor accommodating part 21 ... Electric motor, 21a ... Output gear 25 ... Fixing screw 26 ... Weight (2nd, 3rd embodiment)
DESCRIPTION OF SYMBOLS 30 ... Grip part 31 ... Switch lever 32 ... Main switch 40 ... Magazine 50 ... Power supply part 51 ... Battery attachment part 52 ... Battery pack 53 ... Controller 54 ... Hook 60 ... Drive mechanism 61 ... 1st drive gear 61a ... 1st engagement Roller, 61b ... support shaft 62 ... second drive gear 62a ... second engagement roller, 62b ... auxiliary engagement portion, 62c ... support shaft 70 ... striking mechanism (first embodiment)
71 ... Blowing mechanism (second and third embodiments)
74 ... Blowing mechanism (fourth embodiment)
80 ... Rack and pinion mechanism 80a, 80b ... Gap (backlash)
81 ... Drive-side rack gear 81a ... meshing tooth 82 ... driven-side rack gear 82a ... meshing tooth, 82b ... missing tooth part (third embodiment)
83 ... Drive side pinion gear 83a ... meshing tooth, 83b ... holding hole, 83c ... support hole 84 ... elastic member 85 ... support shaft 86 ... driven side pinion gear 86a ... meshing tooth, 86b ... holding hole, 86c ... support hole 90 ... rack Pinion mechanism (fourth embodiment)
91 ... Drive side rack gear 92 ... Drive side rack gear 93 ... Drive side pinion gear 93a ... Holding hole, 93b ... Support hole 94 ... Drive side pinion gear 94a ... Engagement part, 94b ... Support hole 95 ... Elastic member 96 ... Pinion gear (fourth embodiment) Form)

Claims (9)

An impact driver that moves in the driving direction and hits the driving tool, a weight that moves in the direction opposite to the impact driver, and the weight and the impact driver are interposed between the weight and the impact driver. A driving tool having a rack and pinion mechanism that moves in directions opposite to each other,
The rack and pinion mechanism includes a driving side rack gear on the impact driver side, a driven side rack gear on the weight side, a driving side pinion gear meshed with the driving side rack gear, and a driven side pinion gear meshed with the driven side rack gear. Have
The driving side pinion gear and the driven side pinion gear are supported so as to be coaxial with each other and relatively rotatable within a certain angular range,
A driving tool in which an elastic member that elastically absorbs relative rotation between the driving side pinion gear and the driven side pinion gear is interposed between the driving side pinion gear and the driven side pinion gear. 2. The driving tool according to claim 1, wherein rotational power is transmitted from the driving side pinion gear to the driven side pinion gear through the elastic member. An impact driver that moves in the driving direction and hits the driving tool, a weight that moves in the direction opposite to the impact driver, and the weight and the impact driver are interposed between the weight and the impact driver. A driving tool having a rack and pinion mechanism that moves in directions opposite to each other,
A driving tool configured to allow movement of the weight to the moving end in the counter driving direction after the hitting driver reaches the moving end in the driving direction and stops. The driving tool according to claim 3, wherein
The rack and pinion mechanism includes a driving side rack gear on the impact driver side, a driven side rack gear on the weight side, a driving side pinion gear meshed with the driving side rack gear, and a driven side pinion gear meshed with the driven side rack gear. Have
After at least one of the driving-side rack gear and the driving-side pinion gear or the driven-side rack gear and the driven-side pinion gear, the weight is driven back after the hitting driver reaches the moving end in the driving direction. A driving tool in which a backlash is set so that the weight reaches the moving end in the anti-driving direction while meshing between adjacent meshing teeth by moving in the direction. An impact driver that moves in the driving direction and hits the driving tool, a weight that moves in the direction opposite to the impact driver, and the weight and the impact driver are interposed between the weight and the impact driver. A driving tool having a rack and pinion mechanism that moves in directions opposite to each other,
A driving tool having a moving end damper for restricting a moving end of the weight in the anti-driving direction, and an auxiliary damper for providing elastic resistance with respect to the moving operation of the weight before the moving end damper. 6. The driving tool according to claim 5, wherein an elastic rubber body is used as the moving end damper and a leaf spring is used as the auxiliary damper. 7. The driving tool according to claim 5 or 6, wherein the rack and pinion mechanism includes a driving side rack gear on the impact driver side, a driven side rack gear on the weight side, and a driving side pinion gear meshed with the driving side rack gear. And a driven pinion gear meshed with the driven rack gear, and when the weight is moved in the counter driving direction, the driven pinion gear receives the elastic resistance of the auxiliary damper. Driving tool designed to disengage the side rack gear. The driving tool according to any one of claims 1 to 7, wherein a moving distance of the driving driver and a moving distance of the weight which are made by the rack and pinion mechanism are different from each other. 9. The driving tool according to claim 8, wherein in the rack and pinion mechanism, the number of teeth of the driving side pinion gear that meshes with the driving side rack gear on the impact driver side is equal to the number of teeth of the driven side pinion gear that meshes with the driven side rack gear on the weight side. A driving tool that is set to be larger than the number and the moving distance of the weight is set to be smaller than the moving distance of the impact driver.

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