JP5455153B2 - Spring type driving machine - Google Patents

Description

  The present invention relates to a driving machine, and more particularly, to a spring type driving machine using a spring as power.

  2. Description of the Related Art Conventionally, a driving machine using a storage battery as a power source, pushing up a plunger with a driving force of a motor to compress a coil spring, and accelerating the plunger when released is known.

  As shown in Patent Document 1, this driving machine compresses a coil spring by utilizing the rotation of a motor, opens the coil spring at a predetermined position, rapidly accelerates the plunger and the blade, and hits the driving tool. doing. In order to compress the coil spring, a roller is attached to one end surface of a final gear that is a rotating body driven by a motor, the roller is moved on a circular track by the rotation of the final gear, and the lifting protrusion provided on the side surface of the plunger is a roller. The plunger is lifted upward to compress the coil spring.

  In addition, in order to strike the insert tool one by one, as shown in Patent Document 2, it is necessary for the operator to start the motor by operating a switch and to stop the motor after one stroke is finished. It is important to detect the position of. In a conventional nailing machine, a projection is provided on the other end surface of the final gear, and the position of the final gear is detected by detecting the presence or absence of the projection with a microswitch, thereby detecting the position of the blade. By detecting the rotational position of the final gear with such a configuration, the initial position of the plunger pulling mechanism and the detection of the driving operation can be realized with a single position detection mechanism, which is a rational configuration.

Japanese Patent Publication No. 07-115307 JP 2008-238288 A

  When a position detection mechanism described in Patent Application 2 is applied to a driving machine having a plunger lifting mechanism described in Patent Document 1, a roller is disposed on one end surface of the final gear and a micro switch is disposed on the other end surface. The distance from the micro switch to the roller in the axial direction of the final gear is increased, which becomes a factor of increasing the driving machine body. Generally, the final gear is arranged between the handle and the coil spring. However, since the distance described above increases, the distance from the handle to the central axis of the injection port for firing the driving tool increases. Therefore, it is difficult to suppress the lifting of the driving machine due to the recoil of the nail by hand, and nail floating or the like is likely to occur, which causes deterioration of workability. Therefore, an object of the present invention is to provide a driving machine that is miniaturized and has improved workability.

In order to solve the above-described problems, the present invention provides a housing, a blade for hitting a stopper, a plunger to which the blade is attached, a plunger that is disposed in the housing and can reciprocate on a moving shaft, and the plunger Provided on the plunger, a spring that urges the motor to one side in the movement axis direction, a motor held in the housing, a rotating body that rotates by rotation of the motor and has a latching portion that protrudes in the rotation axis direction, and Extending in a direction crossing the movement axis, and having a hooked portion that is hooked on the hooking portion, and rotating the rotating body to move the plunger to the other side in the movement axis direction, In the spring-type driving machine that compresses the spring, the latching portion includes a pin that includes a base portion that is extended from the end surface and disposed at a position spaced apart from the rotation shaft, and a flange portion that is positioned at the tip of the base portion. The pin mounted on the pin A roller that rotates about a shaft as a rotating shaft, and the roller has a first hole portion whose inner periphery slides on the outer periphery of the flange portion, and a base portion that is communicated with the first hole portion and is inserted through the first hole portion. A second hole that is smaller in diameter than the outer periphery of the flange and larger in diameter than the base is formed , and a plurality of the latching portions are provided on a concentric circle of the rotating body. The amount of protrusion from the end face gradually increases in the rotation direction of the rotating body and the length of the flange portion in the rotation axis direction is increased. The same number as the number of parts is provided so as to be arranged substantially in parallel with the moving shaft, and the amount of protrusion from the moving shaft decreases as it is located on one side in the moving shaft direction. A spring-type driving machine is provided. According to such a configuration, in the latching portion, a large load is applied to the latching portion having a large protrusion amount, but the latching portion having a large projection amount has a large flange portion, so that the gap between the roller portion and the flange portion is large. A large sliding portion can be taken, and deterioration of wear and the like can be suppressed to extend the life. In the hooked portion, a large load is applied to the hook portion having a small protrusion amount. However, since the hook portion having a large load has a small protrusion amount, the moment load from the moving shaft can be reduced.

  Moreover, it is preferable that the edge part of this flange and the edge part of this roller are arrange | positioned in the same position in this latching part in the direction which protrudes from this rotary body.

  According to such a configuration, since it is not necessary to adopt a configuration in which the flange portion that is the tip portion of the pin protrudes from the roller, the amount of protrusion from the end surface of the pin can be reduced. Therefore, it is possible to reduce the size of the driving machine by suppressing the protrusion on the end face side of the rotating body.

  According to the driving machine of the present invention, downsizing can be achieved, and workability can be improved by downsizing.

Side surface sectional drawing of the driving machine which concerns on embodiment of this invention. The figure which shows the rotary body and angular position detection mechanism which concern on embodiment of this invention. Sectional drawing along the III-III line of FIG. It is sectional drawing along the IV-IV line | wire of FIG. 1, (A) The state before rotation, (b) (c) The state which the bumper holder rotated slightly clockwise and counterclockwise. Sectional drawing along the VV line of FIG. The sectional view seen from the (a) one side side of the plunger of the driving machine concerning an embodiment of the invention, (b) The other side side view. The enlarged view of the bumper holder of the driving machine which concerns on embodiment of this invention. The enlarged view of the bumper holder part of the driving device which concerns on embodiment of this invention (The state where the holder side seat surface and the screw part side seat surface adjoined). The sectional view seen from the side of one side of the plunger of the driving machine concerning a comparative example, (b) The other side side view.

  Hereinafter, a driving machine according to an embodiment of the present invention will be described with reference to FIGS. 1 to 8. A nailing machine 1 which is a driving machine shown in FIG. 1 is an electric type, and staples 1A which are stoppers are driven into a material to be driven W such as wood or gypsum board which is a material to be driven. The nailing machine 1 mainly includes a housing 2, a motor 3, a speed reduction mechanism 4, a compression mechanism 5, a coil spring portion 6, a magazine 7, and an angular position detection mechanism 8. A direction in which a plunger 63 to be described later moves is defined as a vertical direction, and a direction in which the plunger 63 is urged by a coil spring 62 that constitutes the coil spring portion 6 to strike the staple 1A is defined as a downward direction. The direction in which the handle 22 extends is defined as a rear direction, and the opposite direction is defined as a front direction.

  The housing 2 is made of a resin such as nylon or polycarbonate. The housing 2 includes a main body 21 mainly including a compression mechanism 5, a coil spring portion 6, and a blade guide 7, a handle 22 extending from an upper portion of the main body 21 in a direction substantially perpendicular to the vertical direction, The motor 3 and the speed reduction mechanism 4 are mainly built in, and are mainly composed of a sub-body 23 that extends from the lower part of the main body 21 substantially parallel to the handle 22.

  A blade guide 26 that holds a later-described driver blade 6A is embedded in the lowermost end portion of the main body 21, and a nose 21A that protrudes downward is provided. In the nose 21 </ b> A, an injection hole 21 a that is a part of a wall that defines the blade guide 26 is formed on the rear surface side of the blade guide 26. The injection hole 21a passes through the main body 21 to a position of a plunger 63 described later. Above the blade guide 26, a cover plate (not shown) located in front of the driver blade 6A described later is disposed. A receiving portion 21 </ b> B that receives the coil spring portion 6 is formed in the lower part of the main body 21 near the nose 21 </ b> A. A lower perforation 21b that opens upward and fits the coil spring portion 6 is formed in a substantially central portion in the receiving portion 21B.

  Further, an upper perforation 21 c that fits with the coil spring portion 6 is formed in the main body 21 above the coil spring portion 6.

  As shown in FIG. 3, an opening 21 d is formed in the main body 21 at a side wall portion and in an upper position in the vicinity of the receiving portion 21 </ b> B, as shown in FIG. 3. As shown in FIG. 4A, a pair of rails 21C and 21C extending in the vertical direction is provided on both side walls on the inner surface of the main body 21 and above the opening 21d. Further, in the vicinity of the opening 21d, a convex portion 21D made of a metal plate and engaged with the outer periphery of the adjuster 66 which is grooved is provided.

  In the main body 21, a push lever 24 that protrudes from the tip of the nose 21 </ b> A and can move up and down with respect to the main body 21 is provided on the front side of the coil spring portion 6. The push lever 24 is configured to retract from the tip of the nose 21 </ b> A by bringing the nose 21 </ b> A into contact with the workpiece and move upward in the main body 21. At the rear end of the push lever 24, an urging member 24A for urging the push lever 24 downward with respect to the main body 21 is disposed. Therefore, the push lever 24 is always in a state of protruding from the nose 21A unless urged upward.

  Further, the push lever 24 has an arm portion 24 </ b> B that extends to the rear side across the coil spring portion 6. In the main body 21, a push switch 24C is disposed above the arm portion 24B, and senses that the push lever 24 has moved upward.

  In the main body 21, a gear holder 25 that holds a planetary gear mechanism 41 and a final gear 42 described later is disposed behind the coil spring portion 6. The gear holder 25 is provided with a support shaft portion 25A that pivotally supports the final gear 42 at a position between the handle 22 and the sub-body 23 in the vertical direction and projects forward with the front-rear direction as the axial direction. A through hole 25a into which the planetary gear mechanism 41 is inserted is formed at the position where the sub body 23 is disposed, with the front-rear direction as the through direction.

  The handle 22 is provided with a trigger 22 </ b> A and a trigger switch 22 </ b> B for controlling the motor 3 at a connection portion with the main body 21. A detachable battery 2 </ b> A is provided at the rear end of the handle 22. Further, in the vicinity of the battery 2A inside the handle 22, the electric power supplied from the battery 2A is supplied to the motor 3 based on the detection results from the push switch 24C, the trigger switch 22B, the detection switch 73 and the micro switch 83 described later. A power supply control unit 2B for controlling and supplying is provided.

  The magazine 7 is arranged on the lower side of the sub body 23 so as to extend in the front-rear direction.

  The motor 3 has a rotating shaft portion 31 and is arranged so that the axial direction of the rotating shaft portion 31 is parallel to the front-rear direction.

  The speed reduction mechanism 4 is disposed coaxially with the motor 3 in front of the motor 3, and mainly includes a planetary gear mechanism 41 and a final gear 42. The planetary gear mechanism 41 is provided at the end position of the rotary shaft portion 31, is mounted in the through hole 25 a and is held by the gear holder 25, and is attached to the rotary shaft portion 31, a sun gear, a revolving gear, and an output This is a known gear mechanism including the gear 41A and the like. The output gear 41 </ b> A of the planetary gear mechanism 41 is arranged coaxially with the rotary shaft portion 31. The final gear 42 meshes with the output gear 41A, is rotatably supported by the support shaft portion 25A, and the distance between the rear end surface of the final gear 42 and the front surface of the gear holder 25 is a plate of the switch lever 82 described later. It is configured to be slightly larger than the thickness. In addition, a projection 42A with which a switch lever 82 described later abuts is provided on the rear end face of the final gear 42. The projecting portion 42A has an arc shape that is arranged over about 180 degrees in the circumferential direction of the final gear 42, and the amount of protrusion from the rear end side surface is slightly smaller than the plate thickness of the switch lever 82 described later. It is configured to be large.

  The compression mechanism 5 includes a first hooking portion 5A and a second hooking portion 5B that protrude from the front end face of the final gear 42, which is a rotating body, toward the front side. As shown in FIG. On the front side of the front side, the first hooking portion 5A is located on the concentric circle centered on the axis of the support shaft portion 25A at an interval of about 120 degrees, and the second hooking portion 5B is located on the rear end side. Is arranged.

  As shown in FIG. 5, the first latching portion 5 </ b> A and the second latching portion 5 </ b> B are each composed of a first pin 51 and a first roller 53, a second pin 52 and a second roller 54 having substantially the same diameter. The second pin 52 and the second roller 54 are configured such that the length in the front-rear direction is larger than that of the first pin 51 and the first roller 53. Further, the first roller 53 and the second roller 54 are engaged with the plunger 63.

  The first pin 51 has a substantially cylindrical first base portion 51A extending from the front end face of the final gear 42, and is disposed on the front side of the first base portion 51A and has a larger diameter than the first base portion 51A and is substantially cylindrical. And a first flange 51 </ b> B that rotatably supports the first roller 53. A width d in the front-rear direction over the circumferential direction of the first base portion 51A is provided at a location connected to the first flange 51B in the first base portion 51A for convenience of processing (it is not easy to form an orthogonal shape). The groove 51a (FIG. 6A) is formed. The first roller 53 is formed in an annular shape from a first hole 53 a and a second hole 53 b that communicate with each other in the front-rear direction, and is rotatably attached to the first pin 51. The first hole 53a is formed in substantially the same shape as the first flange 51B, and is configured such that the inner periphery in the first hole 53a slides with the outer periphery of the first flange 51B. The second hole 53b has a smaller diameter than the first flange 51B and a larger diameter than the first base 51A, and the first base 51A is inserted therethrough. Since the outer periphery of the first flange 51B has a larger diameter than the second hole 53b, the first roller 53 is prevented from falling off from the first pin 51. In the first roller 53, the depth of the first hole 53a is configured to be substantially the same as the length in the front-rear direction of the first flange 51B. Therefore, the front ends of the first flange 51B and the first roller 53 are arranged on the same plane.

  Similarly to the first pin 51 and the first roller 53, the second pin 52 and the second roller 54 also have a second base 52A, a second flange 52B, a groove 52a (FIG. 6A), a first hole 54A, and a second roller. The second roller 54 is supported by the second flange 52B so as to be slidable and rotatable. Since the second hooking portion 5B protrudes from the first hooking portion 5A, the second flange 52B has a greater distance in the front-rear direction than the first flange 51B. Accordingly, the drilling depth of the first hole 54A of the second roller 54 is larger than that of the first hole 53a of the first roller 53. Therefore, the area where the second roller 54 and the second flange 53B contact each other is larger than the area where the first roller 53 and the first flange 51B contact each other.

  As shown in FIG. 1, the coil spring portion 6 mainly includes a shaft 61, a coil spring 62, a plunger 63, a bumper 64, a bumper holder 65, and an adjuster 66, and is configured as a unit from these constituent members. Yes. The shaft 61 is formed in a columnar shape, and a flange portion 61A is provided at the uppermost end, and a position defining portion 61B is defined at the lowermost end. The position defining portion 61B is inserted and fixed in the lower perforation 21b, and the collar portion 61A is inserted and fixed in the upper perforation 21c, whereby the position of the coil spring portion 6 in the housing 2 is accurately defined and used. Occasionally, the shaft 61 is prevented from being displaced with respect to the housing 2. Further, a groove is formed around the circumference of the shaft 61 in the vicinity of the position defining portion 61B at the lower end of the shaft 61, and a C-ring shaped tow 61C is mounted in this groove. In the shaft 61, a coil spring 62, a plunger 63, a bumper 64, and an adjuster 66 are mounted above the tome 61 </ b> C.

  The coil spring 62 is configured by winding a steel wire in a spiral shape, and is disposed on the shaft 61 so that the shaft 61 passes through the coil spring 62. A pair of washers 62B and 62B is mounted on the shaft 61 on the upper side of the coil spring 62, and a ring-shaped elastic body 62A such as a resin is sandwiched between the pair of washers 62B and 62B. . The washer 62B has an inner diameter smaller than the outer diameter of the flange 61A. Therefore, the upper end of the coil spring 62 is restricted from moving upward by the pair of washers 62B and 62B and the elastic body 62A.

  A pair of washers 62B and 62B having the same configuration and an elastic body 62A are also arranged below the coil spring 62. The surging generated in the coil spring 62 is absorbed by the pair of washers 62B and 62B and the elastic body 62A arranged above and below.

  The plunger 63 has a through hole 63 a formed in the vertical direction, the shaft 61 passes through the through hole 63 a and is mounted to be movable up and down with respect to the shaft 61, and is disposed below the coil spring 62. Since a pair of washers 62B, 62B and an elastic body 62A are disposed at the lower end of the coil spring 62, the coil spring 62 is in contact with the coil spring 62 via these washers 62B. In addition, as shown in FIGS. 6A and 6B, the plunger 63 includes a first pulling protrusion 63A and a second pulling protrusion 63B that are hooked portions on the rear surface side in the vertical direction. The protrusions 63 </ b> C are provided on the front side.

  63 A of 1st raising protrusion parts protrude toward the back from the upper end position of the plunger 63 so that the protrusion amount which can be engaged with 5 A of 1st latching parts is taken. The second pull-up protrusion 63B protrudes rearward from the lower end position of the plunger 63 so as to take an amount of protrusion that cannot be engaged with the first hook 5A and can be engaged with the second hook 5B. Yes.

  A driver blade 6A is attached to the protrusion 63C. The driver blade 6A is formed in a long and narrow plate shape, and a hole 6a is formed at the upper end portion. A projection 63C is inserted into the hole 6a and connected to the plunger 63. As shown in FIG. 1, the driver blade 6A is inserted into the injection hole 21a. It is arranged to move up and down. In addition, since there is a cover plate (not shown) on the front side of the driver blade 6A in the injection hole 21a, the driver blade 6A is prevented from moving forward, and therefore the driver blade 6A is prevented from dropping from the protrusion 63C. Is done.

  The bumper 64 is made of a soft rubber or a resin such as urethane, and is disposed below the plunger 63 so as to be in contact with the lower end surface of the plunger 63.

  As shown in FIG. 7, the bumper holder 65 extends downward from a bumper receiving portion 65A having a receiving surface for receiving the bumper 64, and a lower surface of the bumper receiving portion 65A located on the side opposite to the bumper 64 with respect to the receiving surface. Is provided with a male thread portion 65B having a screw advance / retreat direction and a holder side seating surface 65C that is defined on the lower surface of the bumper receiving portion 65A and is a plane orthogonal to the vertical direction. The bumper holder 65 is formed with a through-hole 65a extending vertically through the bumper receiving portion 65A and the male screw portion 65B. Therefore, the bumper holder 65 is mounted so that the shaft 61 passes through the through-hole 65 a and can move up and down with respect to the shaft 61.

  As shown in FIG. 4A, the outer peripheral portion of the bumper receiving portion 65A is processed into two surfaces 65D and 65D, and these surfaces 65D and 65D are formed in both side walls of the main body 21. A bumper holder 65 is arranged in the main body 21 so as to be sandwiched between the formed rails 21C and 21C. The distance from one surface 65D to the other surface 65D is configured to be slightly shorter than the distance from the rail 21C in one side wall of the main body 21 to the rail 21C in the other side wall. Therefore, the bumper holder 65 has a slight backlash in the main body 21 and can move up and down smoothly. Since there is a backlash between the main body 21 and the bumper holder 65, the bumper holder 65 does not rotate, for example, 180 ° with respect to the main body 21, but as shown in FIGS. 4B and 4C. Further, it is allowed to rotate at a slight angle of about 10 °.

  As shown in FIG. 7, the male screw portion 65B is formed according to the same standard as the M12 screw. Further, the through hole 65a is formed so that the hole diameter is smaller than the outer diameter of the tome 61C attached to the shaft 61.

  The adjuster 66 is formed in an annular shape, and is provided with a female screw portion 66A that is screwed to the male screw portion 65B on the inner peripheral portion, and a screw portion side seating surface 66B that faces the holder side seating surface 65C is defined on the upper surface. Groove processing is performed on the outer peripheral portion, and the lower surface is in contact with the receiving portion 21B of the main body 21 so that the outer peripheral portion is exposed from the opening 21d (FIG. 3). Further, since the adjuster 66 is screwed with the male screw portion 65B of the bumper holder 65 by the female screw portion 66A, the bumper holder 65 is moved to the adjuster 66 by rotating the adjuster 66 clockwise or counterclockwise with respect to the bumper holder 65. On the other hand, it can move up and down. As shown in FIG. 3, the adjuster 66 is fitted in the housing 2, and the outer periphery engages with the convex portion 21 </ b> D. Therefore, unintended rotation of the adjuster 66 is suppressed.

  As described above, since the adjuster 66 is in contact with the receiving portion 21 </ b> B of the housing 2, the bumper holder 65 screwed with the adjuster 66 moves upward with respect to the adjuster 66, thereby It will move upward. As described above, since both ends of the shaft 61 are fixed to the housing 2, the bumper holder 65 that moves upward relative to the housing 2 moves upward relative to the shaft 61. A bumper 64 is provided on the bumper holder 65, and the bumper 64 is a place where the plunger 63 abuts and defines the bottom dead center of the plunger 63. Further, since the driver blade 6A is mounted on the plunger 63, the bottom dead center position of the driver blade 6A, that is, the driving depth of the driver blade 6A into the workpiece W is changed by the rotation operation of the adjuster 66. be able to.

  Further, as shown in FIG. 7, an O-ring 67 through which the shaft 61 passes is disposed between the holder side seating surface 65C and the screw portion side seating surface 66B. The O-ring 67 is made of an elastic body such as rubber, and its surface is coated with grease for preventing wear.

  As described above, when the coil spring 62, the plunger 63, the bumper 64, the bumper holder 65, the adjuster 66, and the O-ring 67 are attached to the shaft 61 and the tomewa 61C is fitted, the coil spring 62 to the O-ring 67 are connected to the shaft. It is prevented from dropping from 61. Therefore, the shaft 61 to the O-ring 67 are unitized. As described above, the shaft 61 is inserted into the lower perforation 21b and the upper perforation 21c, and fixed to the housing 2 so that the coil spring 62 to the O-ring 67 are similarly installed. Mounted on the housing 2.

  As shown in FIG. 1, the magazine 7 is mainly composed of a holder 71, a pusher 72, and a detection switch 73, and the direction in which the pusher 72 described later urges the staple 1A is parallel to the front-rear direction. Further, it is disposed below the sub body 23. The holder 71 holds a plurality of aligned staples 1A, and the front end of the holder 71 is positioned at the rear side of the blade guide 26 in the ejection hole 21a. Therefore, the staple 1A is supplied to the rear position of the blade guide 26 in the ejection hole 21a.

  The pusher 72 is attached to the holder 71 and biased forward by a spring (not shown), and is disposed behind the plurality of staples 1A. Therefore, the plurality of staples 1A are sequentially supplied into the ejection holes 21a. Further, at the rear end portion of the pusher 72, a piece portion 72A that can come into contact with the detection switch 73 is provided.

  The detection switch 73 is disposed on the sub body 23 located above the holder 71, and abuts against the one portion 72A when the pusher 72 moves to a predetermined position (for example, a position where the number of remaining staples 1A becomes one). It is configured as follows.

  As shown in FIG. 2, the angular position detection mechanism 8 includes a lever pin 81, a switch lever 82, and a micro switch 83. The lever pin 81 is mounted on the front surface of the gear holder 25 and above the final gear 42 with the front-rear direction as the axial direction. The switch lever 82 is pivotally supported by the lever pin 81 and is movable between a contact position where the switch lever 82 comes into contact with the protrusion 42A and a non-contact initial position with the protrusion 42A, as shown in FIG. As described above, the metal plate having a thickness smaller than the protruding amount of the protruding portion 42A is bent to form a substantially L shape. The switch lever 82 is a piece having a substantially L-shaped cross-section, and a protrusion abutting portion 82A is defined on a plate portion orthogonal to the front-rear direction, and a plate that is substantially L-shaped and parallel to the front-rear direction. The detection part contact part 82B is prescribed | regulated to the part.

  The projecting portion abutting portion 82A is disposed in the gap between the gear holder 25 and the final gear 42 so as to be able to abut on the projecting portion 42A. Since the gap between the gear holder 25 and the final gear 42 is slightly larger than the thickness of the protruding portion abutting portion 82A, the protruding portion abutting portion 82A is prevented from being displaced from the protruding portion 42A. . Further, as shown in FIG. 2, the protruding portion abutting portion 82A has a curved outer shape, and the curved shape is configured to contact the protruding portion 42A.

  As shown in FIG. 5, the detector contact portion 82 </ b> B is disposed so as to face the outer periphery of the final gear 42 in the radial direction of the final gear 42.

  The micro switch 83 is provided above the detection unit abutting portion 82B and includes a switch 83A that is biased when the switch lever 82 moves to the abutting position. Since the switch 83A is biased by a spring (not shown), when the contact state between the switch lever 82 and the projection 42A is released, the switch lever 82 can be brought into contact with the projection 42A (initial position). Can be pushed back to. According to such a configuration, since the force with which the switch lever 82 is urged by the protrusion 42 is minimized, wear of the switch lever 82 and the protrusion 42 can be suppressed, and the life can be extended. Further, the switch lever 82 can be reliably returned to the initial position without increasing the number of parts. In addition to the reaction force of the switch 82A, for example, a spring or the like that biases the switch lever 82 toward the initial position may be interposed between the switch lever 82 and the gear holder 25.

  When working with the nailing machine 1 having the above-described configuration, first, the adjuster 66 is rotated in accordance with the driven member W into which the staple 1A is driven, and the driving depth of the staple 1A is adjusted. Thereafter, the tip of the nose 21A is brought into contact with the driven member W, the push lever 24 is moved backward with respect to the housing 2, and the push switch 24C is turned on. Before and after this operation, the trigger 22A is pulled and the trigger switch 22B is turned on. The power supply control unit 2B supplies power to the motor 3 to drive it by detecting an on signal from the push switch 24C and an on signal from the trigger switch 22B.

  As the motor 3 rotates, the final gear 42 rotates. First, the first latching portion 5A and the first pulling protrusion 63A are engaged, and the plunger 63 is moved upward. In a state where the final gear 42 further rotates and the plunger 63 has moved upward, the second hooking portion 5A and the second pulling protrusion 63B are next engaged, and the second hooking portion 5B is moved to the plunger 63. Is moved further upward. Engagement between the first locking part 5A and the first lifting protrusion 63A occurs when the engagement between the second locking part 5B and the second lifting protrusion 63B occurs and the plunger 63 moves upward. Is solved.

  When the final gear 42 further rotates from this state, the second locking portion 5B is separated from the second pulling protrusion 63B due to the circular motion of the second hooking portion 5B. When the plunger 63 moves upward, elastic energy is accumulated in the coil spring 62 and the plunger 63 is urged by the coil spring 62. In this state, when the second locking portion 5B is separated from the second pulling protrusion 63B, the plunger 63 suddenly moves downward, and accordingly, the staple 1A is hit by the driver blade 6A, and the covered portion is covered. The staple 1A is driven into the driving material W.

  The rotation state of the final gear 42 is determined by the power control unit 2B based on a detection signal from the micro switch 83 based on the contact between the switch lever 82 and the micro switch 83. Specifically, the protrusion 42A is arranged so that the contact state between the switch lever 82 and the protrusion 42A is eliminated at the same time as the second locking portion 5B is separated from the second pulling protrusion 63B. Accordingly, the switch lever 82 simultaneously moves from the contact position to the initial position, and an off signal is output from the micro switch 83. In a state where the switch lever 82 and the protrusion 42A are in contact with each other, an on signal is output from the micro switch 83, so that the power control unit 2B supplies the motor 3 with the switching from the on signal to the off signal. By stopping the power to be used, the final gear 42 is prevented from excessively rotating.

  Further, when the staple 1A continues to be struck and the remaining amount is reduced, the piece 72A of the pusher 72 comes into contact with the detection switch 73, and an ON signal is output from the detection switch 73. When the power control unit 2B detects a signal from the detection switch 73, even if the ON signal from the trigger switch 22B and the push switch 24C is detected, power supply to the motor 3 is not performed. As a result, idling in the absence of the staple 1A is suppressed.

  Further, in the state where the driving depth of the staple 1A is the deepest, that is, in the state where the bumper receiving portion 65A of the bumper holder 65 is moved closest to the adjuster 66 by rotating the adjuster 66, the holder side seating surface 65D and the screw side seat. Since the O-ring 67 is interposed between the surface 66B, the holder side seating surface 65D and the screw portion side seating surface 66B do not directly contact each other as shown in FIG.

  When the first locking portion 5A and the second locking portion 5B move the first pulling protrusion 63A and the second pulling protrusion 63B upward, respectively, the first locking portion 5A and the second locking portion Since the stop portion 5B is provided on the final gear 42 that moves in a circular motion, the first pulling projection portion 63A and the second pulling projection portion 63B are moved up and down from the first locking portion 5A and the second locking portion 5B. The force which moves to the direction orthogonal to a direction and the front-back direction acts. In the first locking portion 5A and the second locking portion 5B, the first roller 53 and the second roller 54 are in contact with the first lifting protrusion 63A and the second lifting protrusion 63B, respectively. When the locking portion 5A and the second locking portion 5B move the first pulling projection 63A and the second pulling projection 63B upward, the first roller 53 and the second roller 54 are the first By rotating with respect to the pin 51 and the second pin 52, the first and second protrusions 63A and 63B, and the first and second engaging portions 5A and 5B with respect to the first and second protrusions 63A and 63B. Is allowed to move in a direction perpendicular to.

  When the coil spring 62 is compressed as described above, the elastic energy accumulated in the coil spring 62 is larger than that when the first locking portion 5A and the second pulling protrusion 63A are engaged with each other. And the second pulling protrusion 63B are larger when engaged. Therefore, the biasing force received from the plunger 63 is greater in the second locking portion 5B than in the first locking portion 5A.

  When the first roller 53 and the second roller 54 rotate with respect to the first pin 51 and the second pin 52 as described above, the inner circumferences of the first holes 53b and 54b, the first flange 51B, The outer periphery of the two flanges 52B slides. As described above, since the urging force received by the second locking portion 5B is larger than that of the first locking portion 5A, the first hole is larger than the load generated between the inner surface of the first hole 53b and the outer periphery of the first flange 51B. The load generated between the inner surface of 54b and the outer periphery of the second flange 52B becomes larger. However, as described above, the first hole 54b and the second flange 52B have a greater distance in the front-rear direction than the first hole 53b and the first flange 51B. The inner surface of the first hole 53b and the outer periphery of the first flange 51B and the inner surface of the first hole 54b and the outer periphery of the second flange 52B can be made substantially the same.

Moreover, as a comparative example with respect to the present embodiment, the first and second locking portions and the first and second pull-up projection hooks according to the conventional configuration are shown in FIGS. In the first locking portion 105A and the second locking portion 105B in FIG. 9A, in the first pin 151 and the second pin 152, the first roller 153 and the second roller 154 are provided on the first base portions 151A and 152A, respectively. The first roller 153 and the second roller 154 are prevented from coming off by the first flange 151B and the second flange 152B that are mounted so as to be slidably rotatable and provided at the tips of the first bases 151A and 152A. Therefore, the front ends of the first pin 151 and the second pin 152 are located on the front side with respect to the front ends of the first roller 153 and the second roller 154. In addition, a groove 151a having a width d is formed at the boundary between the first base portion 151A and the first flange 151B for the same processing convenience as in the present embodiment, and a similar groove 152a is also formed in the second base portion 152A. Has been. The distance the front-rear direction of the first flange 151B is defined as _{t 1,} the longitudinal length of the second flange 152B is defined as _{t 2.}

  This comparative example is substantially the same as the present embodiment except for the configuration relating to the first locking portion 105A and the second locking portion 105B, and the first pulling protrusion portion 163A and the second pulling protrusion portion 163B. The composition is taken. In the comparative example, the first roller 153 and the second roller 154 are configured to have the same outer shape and longitudinal length as the first roller 53 and the second roller 54 according to the present embodiment.

  In this comparative example and this embodiment, the distance from the shaft to the final gear is compared. In the comparative example and the present embodiment, the distances between the engaging positions of the first and second rollers and the first and second lifting protrusions in the front-rear direction are equal. Yes.

As shown in FIG. 6B, in the present embodiment, the distance from the shaft 61 to the front end surface of the final gear 42 is defined as L, and the second roller 54 that is the front end surface of the compression mechanism 5 from the shaft 61. the distance to the front end is defined as L _1, the distance from the second roller 54 forward to the second lifting protrusion 63B rear end is defined as L _2, the first locking from the second lifting protrusion 63B rear end the distance to the first roller 53 the front end is a front end surface of the part 5A is defined as L _3, the distance from the first roller 53 forward to the first lifting projection portions 63A rear is defined as L _4, the first argument the distance from the upper projections 63A rear to the front end face of the final gear 42 is defined as L _5. Therefore, the sum of L _{1 to} L ₅ is L.

Similarly, as shown in FIG. 9B in the comparative example, the distance from the shaft 161 to the front end surface of the final gear 142 is defined as L ′, and the second flange that is the front end surface of the compression mechanism 5 is defined from the shaft 161. The distance from the front end of 152B is defined as L′ ₁ , the distance from the front end of the second flange 152B to the rear end of the second pulling protrusion 163B is defined as L′ _2, and the distance from the rear end of the second pulling protrusion 163B to the first The distance from the front end of the first flange 151B, which is the front end face of the one locking portion 105A, is defined as L' _3, and the distance from the front end of the first flange 151B to the rear end of the first pulling projection 163A is defined as L' _4. The distance from the rear end of the first pulling protrusion 163A to the front end surface of the final gear 42 is defined as L′ ₅ . Therefore, the sum of L ′ _{1 to} L ′ ₅ becomes L ′.

The distance L ₁ is a necessary gap between the shaft 61 and the compression mechanism 5, and this value is equal to the distance L ′ ₁ (L ₁ = L ′ ₁ ).

The distance L _2, the distance of the second lifting protrusion 63B and the second locking portion 5B overlap the front end of the second locking portion 5B is for equal front end of the second roller 54, the distance L ₂ is The distance between the second pulling projection 63B and the second roller 54 in the front-rear direction is a distance. On the other hand, the distance L ′ ₂ is a distance where the second pulling protrusion 163B and the second locking part 105B overlap, and the distance at which the second pulling protrusion 163B and the second roller 154 are engaged with each other. It is represented by the sum of the longitudinal direction of the distance t ₂ of the second flange 152B. Here, in the present embodiment and the comparative example, the distance between the portions where the second roller and the second lifting protrusion are engaged is equal, and therefore, the distance L ′ ₂ = L ₂ + t ₂ .

The distance L ₃ is a gap necessary so that the second pull-up protrusion 63B and the first locking portion 5A do not come into contact with each other, and this value is equal to the distance L ′ ₃ (L ₃ = L ' ₃ ).

The distance L _4, the distance of the first lifting projection portion 63A and the first locking portion 5A overlaps the front end of the first locking portion 5A is for equal front end of the first roller 53, the distance L ₄ is a The distance is such that the first pulling projection 63A and the first locking portion 5A are engaged in the front-rear direction. On the other hand, the distance L ′ ₄ is a distance where the first pulling protrusion 163A and the first locking part 105A overlap, and the distance between the first pulling protrusion 163A and the first roller 153 is engaged. It is represented by the sum of the longitudinal direction of the distance t ₁ of the first flange 151B. Here, in the present embodiment and the comparative example, the distance between the portions where the first roller and the first pulling protrusion are engaged is equal, so the distance L ′ ₄ = L ₄ + t ₁ .

The distance L ₅ represents a necessary clearance to the first lifting projection portion 63A and the final gear 42 are not in contact, the value 'a value equal to _{5 (L 5 =} L' distance L _5).

From these relationships, a relational expression of L = L ′ − (t ₁ + t ₂ ) is derived. Therefore, in the present embodiment, the distance from the shaft 61 to the final gear 42 (final gear front surface distance) is compared with the comparative example. , T ₁ + t ₂ can be shortened.

  In addition, since the angular position detection mechanism 8 is disposed above the final gear 42, there is a gap between the final gear 42 and the gear holder 25, as described above, in which the protrusion contact portion 82A of the switch lever 82 enters. Therefore, the distance from the final gear 42 to the gear holder 25 can be shortened. Therefore, the main body 21 can be made smaller by shortening these distances.

In FIG. 6B, the protrusion amounts l ₁ and l ₂ of the base end portions of the first and second pull-up protrusions 63A and 63B are l ₁ = L ₁ −l ₀ + L ₂ + L ₃ + L _{4, respectively.}
l ₂ = L ₁ −l ₀ + L ₂
Given in. Here, the distance ₁₀ is a distance from the shaft 61 to the base end portions of the first and second pulling protrusions 63A and 63B.

Similarly, in FIG. 9B, the protrusion amounts l ′ ₁ and l ′ ₂ of the base end portions of the first and second pulling protrusions 163A and 163B are l ′ ₁ = L ′ ₁ −l ′ ₀ + L ′, respectively. ₂ + L ′ ₃ + L ′ ₄
l ′ ₂ = L ′ ₁ −l ′ ₀ + L ′ ₂
Given in.

In the present embodiment and the comparative example, the distances l ₀ and l ′ ₀ from the shaft to the base end positions of the first and second lifting protrusions are the same in the configuration of the plunger and the like, so that l ₀ = l 'is equal to ₀ .

In this relational expression, if the difference between the protrusion amount l ′ ₁ and the protrusion amount l ₁ and the difference between the protrusion amount l ′ ₂ and the protrusion amount l ₂ are taken, l ′ ₁ −l ₁ = t ₁ + t ₂ , l A relational expression of ' ₂ -l ₂ = t ₂ is obtained. Therefore, the first and second lifting projections 63A and 63B according to the present embodiment can be made shorter in projection amount than the first and second lifting projections 163A and 163B according to the comparative example.

  The first and second pull-up protrusions 63A and 63B are extended from the rear surface of the plunger 63 to form a cantilever shape, and the end portions of the cantilever shape are the first locking portions 5A and the second. The locking portion 5B is biased upward so as to lift. When such a force is applied, a moment around the axis orthogonal to the axis of the shaft 61 is generated in the plunger 63, and friction is generated between the inner surface of the through hole 63a and the outer peripheral surface of the shaft 61. On the other hand, in the present embodiment, since the protrusion amounts of the first and second pulling protrusions 63A and 63B are reduced, the above-described moment can be reduced. Therefore, the friction generated between the inner surface of the through hole 63a and the outer peripheral surface of the shaft 61 can be reduced, and the plunger 63 can be smoothly moved up and down with respect to the shaft 61.

  Further, in the present embodiment, in FIG. 6A, for example, the first flange 51B and the groove 51a are positioned below the portion of the first roller 53 that contacts the first pulling protrusion 63A. There is no. On the other hand, in the comparative example, in FIG. 9A, the groove 151a is located below the portion of the first roller 153 that contacts the first pulling protrusion 163A. Therefore, according to this Embodiment, the sliding location which generate | occur | produces between a roller and a pin can be taken long in the front-back direction, and the lifetime improvement of a pin and a roller can be achieved.

  Further, in the driving machine 1, since the handle 22 is not positioned on the shaft 61, a moment is generated in the handle 22 so that the main body 21 moves upward due to the reaction during driving. However, as described above, since the size is reduced and the handle 22 is brought close to the shaft 61, the generated moment can be reduced. Therefore, the reaction force generated in the handle 22 can be reduced, and the workability of the driving machine 1 can be increased.

1 .. Nailing machine 1A .. Staple 2. Housing 2A.. Battery 2B.. Power source control unit 3. Motor 4. Reduction mechanism 5 ... Compression mechanism 5A ... 1st latching part 5B ... Double latching part 6 .. Coil spring part 6 A... Driver blade 6 a... Hole 7... Magazine 8 .. Angular position detection mechanism 21 .. Main body 21 A ・ Nose 21 B ・ Receiving part 21 C ・ Rail 21 </ b> D Convex part 21a ... Injection hole 21b ... Lower drilling 21c ... Upper drilling 21d ... Opening 22 ... Handle 22A ... Trigger 22B ... Trigger switch 23 ... Subbody 24 ... Push lever 24A ... 24B ·· Arm portion 24C · · Push switch 25 · · Gear holder 25A · · Support shaft portion 25a · · Through hole 26 · · Blade guide 31 · · Rotary shaft portion 41 · · Planetary A mechanism 41A .... output gear 42..final gear 42A..projection 51..first pin 51A..first base 51B..first flange 52..second pin 52A..second base 52B .. Second flange 53 ·· First roller 53A · · First hole 53b · · Second hole 54 · · Second roller 54A · · First hole 54b · · Second hole 61 · · Shaft 61A · · · flange 61B · · Position defining portion 61C · · Tomewa 62 · · Coil spring 62A · · Elastic body 62B · · Washer 63 · · Plunger 63A · · first pulling protrusion 63B · · second pulling protrusion 63C · · protrusion 63a · -Through hole 64-Bumper 65-Bumper holder 65A-Bumper receiving part 65B-Male screw part 65C-Holder side seating surface 65D-Face 65a-Through hole 66-Adjuster 66A-Female screw part 6B ... Screw side seating surface 67 ... O-ring 71 ... Holder 72 ... Pusher 72A ... Single piece 73 ... Detection switch 81 ... Lever pin 82A ... Projection part contact 82B ... Detection part contact 82 ・ ・ Switch lever 83 ・ ・ Micro switch

Claims (2)

A housing;
A blade that strikes the stop;
A plunger that is mounted on the blade and is reciprocated on a moving shaft disposed in the housing;
A spring that biases the plunger toward one side in the movement axis direction;
A motor held in the housing;
A rotating body that has a latching portion that is rotated by the rotation of the motor and protrudes in the direction of the rotation axis;
The plunger is provided with a hooked portion that extends in a direction intersecting the moving shaft and is hooked by the hooking portion, and the rotating body rotates to move the plunger to the other side in the moving axis direction. In a spring-type driving machine that moves to and compresses the spring,
The latching portion includes a pin that includes a base portion that extends from the end surface and is spaced apart from the rotation shaft, and a flange portion that is positioned at the tip of the base portion, and is attached to the pin and rotates the shaft of the pin A roller that rotates as a shaft, and the roller has a first hole portion whose inner periphery slides on the outer periphery of the flange portion, a base portion that is communicated with the first hole portion and the flange portion. A second hole having a smaller diameter than the outer periphery and a larger diameter than the base is formed ,
A plurality of the latching portions are provided on a concentric circle of the rotating body,
The plurality of latching portions are configured such that, in the rotation direction of the rotating body, the amount of protrusion from the end surface gradually increases and the length of the flange portion in the rotation axis direction is increased.
The hooked portion is provided so that the same number as the number of the plurality of hooking portions is arranged substantially in parallel with the moving shaft, and the amount of protrusion from the moving shaft becomes closer to one side in the moving shaft direction. A spring-type driving machine characterized in that it is configured to be small . The spring-type driving machine according to claim 1 , wherein the end of the flange and the end of the roller are arranged at the same position in the direction in which the latching part protrudes from the rotating body. .

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