JP2011067925A - Driving machine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a highly handlable driving machine in which rotation torque of an operation unit does not vary in driving. <P>SOLUTION: The driving machine is equipped with: a housing 2; a blade 6A for striking a staple 1A; a plunger 63 on which the blade 6A is mounted; a bumper 64 provided on a moving shaft of the plunger 63 against which the plunger 63 collides to have a bottom dead center defined; a bumper holder 65 having a receiving surface 65A for receiving the bumper 64, an external threaded part 65B, and a holder-side bearing surface 65C; an adjuster 66 having an internal threaded part 66A to be screwed with the external threaded part 65B and a screw-side bearing surface 66B facing the holder-side bearing surface 65C, and rotating around the moving shaft with respect to the bumper holder 65 to define a position of the bumper holder 65 in the direction of the moving shaft; and an O-ring 67 provided between the holder-side bearing surface 65C and the screw-side bearing surface 66B. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a driving machine.

  2. Description of the Related Art Conventionally, a driving machine that uses a storage battery as a power source, pushes up a plunger with a driving force of a motor to compress a coil spring, and accelerates and drives the plunger when released is known (see, for example, Patent Document 1 and Patent Document 2). ).

  This driving machine compresses a coil spring by utilizing rotation of a motor, opens the coil spring at a predetermined position, rapidly accelerates a plunger and a blade, and hits a driving tool. After the impact, the plunger collides with the bumper, the remaining kinetic energy consumed by the impact is absorbed, and the plunger and the blade are stopped. During this time, the blade jumps out of the main body injection port by an arbitrary amount, and pushes the driving tool into the driven material.

  In order to adjust the driving depth of the driving tool, a method of adjusting the distance between the main body and the driven material at the time of driving by adjusting the length of the push lever or the position with respect to the main body is common. A bumper holder that holds the bumper and is movable in the striking direction with respect to the housing; and an adjuster that is an operation unit that rotates the bumper holder by rotating relative to the housing. The adjuster is rotated to move the bumper holder to a predetermined position. There are known methods of arranging them.

Japanese Patent Publication No. 07-115307 Japanese Patent Laid-Open No. 04-122581

  When the bumper and the plunger collide, an impact load is generated in the collision direction. Since the impact load acts on the screwed portion of the bumper holder and the adjuster, the bumper holder rotates relative to the adjuster so that the bumper holder moves in the striking direction according to the slope direction of the screw. When the surface of the bumper holder that faces the adjuster and the surface of the adjuster that faces the bumper holder are in contact with each other, the so-called “catch-up” is further rotated by the impact load. If the tightening occurs, the turning torque of the adjuster suddenly increases according to the spring constant of the material, and the operator may not be able to easily rotate the adjuster. Therefore, an object of the present invention is to provide a driving machine with good operability, in which the turning torque of the operation unit does not change during driving.

  In order to solve the above-described problems, the present invention provides a housing, a blade that strikes a stopper, a plunger that is mounted on the blade and that is disposed in the housing and can reciprocate on a moving shaft, and the movement A bumper which is disposed on the shaft and defines the one-side dead center in the axial direction when the plunger collides, a receiving surface which receives the bumper, and an anti-bumper side which is positioned on the opposite bumper side with respect to the receiving surface. A bumper holder having a first screw portion in a direction, a holder side seating surface located on the side opposite to the bumper with respect to the receiving surface, a second screw portion screwed with the first screw portion, and the holder side seat A screw member facing the surface and having a threaded portion side seating surface, rotating about the movement axis relative to the bumper holder to define a position of the bumper holder in the movement axis direction, the holder side seating surface and the screw portion An elastic body disposed between the side seating surface and To provide a machine.

  In the driving machine configured as described above, the bumper holder is rotatably held by the housing in a range of a certain rotation angle around the movement axis, and the screw member is rotatable around the movement axis and moved. It is preferable that the housing is held so as not to move to one side in the axial direction.

  The housing is provided with an opening through which a part of the screw member is exposed to the outside. The screw member is provided with an operation portion for rotating the screw member on an outer periphery around the moving shaft. It is preferable to expose from the opening.

  According to such a configuration, even when the impact load is applied and the bumper holder and the screw member rotate relatively, the elastic body is interposed between the holder side seating surface and the screw part side seating surface, Contact is prevented. Therefore, it is possible to prevent the tightening that the rotation torque between the bumper holder and the screw member is suddenly increased.

  The spring constant related to the displacement of the elastic body in the moving axis direction is preferably smaller than the spring constants of the bumper holder and the screw member when the holder side seating surface is in contact with the screw part side seating surface. .

  According to such a configuration, the frictional force generated between the bumper holder and the screw member via the elastic body is smaller than the frictional force generated when the bumper holder and the screw member are in direct contact. The rotational torque is difficult to increase and the operability is improved.

  Further, it is preferable that the elastic body is in the elastic deformation region in a state in which a rotational torque is applied to the screw member so that the holder side seating surface and the screw portion side seating surface are close to each other.

  According to such a configuration, in a state where the screw member is tightened, the rotational torque does not change excessively, and the operability is improved.

  The first screw is formed of a male screw and protrudes from the holder side seating surface toward one end in the moving axis direction, and the second screw portion is formed of a female screw and is formed on the screw unit side seating surface. It is preferable that an opening of the female screw is formed.

  According to the driving machine of the present invention, the turning torque of the operation unit does not change during driving and the operability can be improved.

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. (A) One side view of the plunger of the driving machine which concerns on embodiment of this invention, (b) Sectional drawing seen from the other side surface. 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). Explanatory drawing of the follow-up of the nail driver which concerns on embodiment of this invention. Explanatory drawing of the catch-up in a comparative example.

  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 portion of the main body 21 in the vicinity of 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 an 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. 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 are configured to include a second base 52A, a second flange 52B, a first hole 54A, and a second hole 54b. A roller 54 is slidably supported on the second flange 52B. 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. Furthermore, it is allowed to rotate at a slight angle of about 10 ° which is a constant rotation angle.

  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 protrusion 42A is released, the switch lever 82 can be pushed back from the contact position to the initial position.

  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. As a result, 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.

  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 striking is performed in this state, a downward impact is generated on the bumper holder 65 due to the collision of the plunger 63 with the bumper 64. In this state, the adjuster 66 is not rotated with respect to the housing 2 because the rotation is restricted by the convex portion 21 </ b> D. Since the bumper holder 65 can be slightly rotated with respect to the housing 2 as described above, the bumper holder 65 is additionally clamped against the adjuster 66 by the impact described above. However, as described above, since the O-ring 67 is interposed between the bumper holder 65 and the adjuster 66, as shown in FIG. It is suppressed that 65D and the screw part side seating surface 66B contact | abut, and are tightened up.

Here, in the case where the O-ring 67 is present and not present, as shown in FIGS. 4B and 4C, the case where the bumper holder 65 is slightly rotated with respect to the adjuster 66 by the follow-up tightening will be compared. . FIG. 9 shows an explanatory diagram of the closing state according to the embodiment of the present invention. FIG. 9A is a cross section obtained by cutting the bumper holder 65 and the adjuster 66 along a plane extending in the vertical and front-rear directions, and FIG. 9B is a cross section obtained by cutting the O-ring 67 along a plane perpendicular to the vertical direction. The spring constant k _{1 of} the O-ring 67 and the thickness L _{1 in} the vertical direction of the O-ring 67 are defined. The spring constant k ₁ of the O-ring 67 is determined by the longitudinal elastic modulus E _{1 of} the material used as the base material of the O-ring 67 and the cross-sectional area A ₁ of the O-ring 67. At the time of tightening, as shown in FIG. 9A, the O-ring 67 having the thickness L ₁ receives the compression deformation δ ₁ and applies a deformation load f ₁ (= k ₁ × δ ₁ ) proportional to the spring constant k _1. Arise. Further, since a frictional force μ ₁ f ₁ proportional to the deformation load f ₁ is generated at a position where the center radius R ₁ is taken on the contact surface of the O-ring 67, the adjuster 66 can be rotated in a state in which the tightening occurs. The necessary rotation torque T ₁ is T ₁ = μ ₁ f ₁ × R ₁ = μ ₁ k ₁ δ ₁ R ₁ . Here, the center radius R ₁ is the distance from the center of the O-ring 67 to the center in the radial direction of the O-ring 67 cross section.

Next, FIG. 10 shows an explanatory diagram at the time of a follow-up with no O-ring as a comparative example. FIG. 10A is a cross-sectional view taken along a plane extending in the vertical and forward and backward directions of the bumper holder 65 and the adjuster 66, and FIG. 10B is a contact portion between the holder portion side seating surface 65C and the screw portion side seating surface 66B and the male screw portion 65B. It is a cross section with. The spring constant k _{2 of} the male screw portion 65B and the length L ₂ in the vertical direction of the male screw portion 65B are defined. The spring constant k ₂ of the male screw portion is determined by the longitudinal elastic modulus E ₂ of the bumper holder 66 and the cross-sectional area A ₂ of the male screw portion. At the time of retightening, the male screw portion having a length L ₂ causes a tensile deformation δ ₂ , and a deformation load f ₂ (= k ₂ × δ ₂ ) proportional to the spring constant k ₂ . Further, since a frictional force μ ₂ f ₂ proportional to the deformation load f ₂ is generated at a position where the center radius R ₂ on the contact surface of the adjuster 66 is taken, the adjuster 66 can be rotated in a state in which the tightening occurs. The necessary rotational torque T ₂ is T ₂ = μ ₂ f ₂ × R ₂ = μ ₂ k ₂ δ ₂ R ₂ . Wherein the central radius R ₂ from the center of the holder-side seat surface 65C and the screw portion side seating surface 66B, the distance to the center in the radial direction of the contact portion of the holder portion side seat surface 65C and the screw portion side seating surface 66B is there.

Compare with actual values based on the above definition. The spring constant of the O-ring 67 is k ₁ = 181 N / mm, and the male thread portion of the bumper holder 66 is k ₂ = 1280 × 10 ³ N / mm. The friction coefficients are μ ₁ = 0.2 and μ ₂ = 0.2. Then, the respective displacement amounts are set as δ ₁ = 0.05 mm and δ ₂ = 0.05 mm, which are the movement amounts of the bumper holder in the present invention. The center radii are R ₁ = 5.75 mm and R ₂ = 7.5 mm. At this value, the rotational torque in the embodiment is T ₁ = 10.4 Nmm. In addition, the rotational torque in the comparative example is T ₂ = 96000 Nmm. In this comparative example, the operator cannot adjust the adjuster 66.

  The rotational torque normally input by the operator to the adjuster 66 was measured and found to be 140 Nmm. Therefore, the maximum rotation torque that can be input by the operator is set to 420 Nmm, which is three times the actual measurement value (140 Nmm). The amount of movement of the bumper holder 65 when the adjuster 66 is rotated at the maximum rotational torque of 420 Nmm, that is, the amount of compression of the O-ring 67 is calculated to be 0.8 mm. Even if 0.05 mm is added, the bumper holder 65 and the adjuster 66 do not come into contact with each other. Further, in this displacement amount, the O-ring 67 is in the elastic deformation region. That is, even if the operator turns the adjuster strongly by hand, the adjuster (screw member) and the bumper holder are not fixed.

  Further, the increase in the rotational torque of the adjuster 66 is 10.4 Nmm in the embodiment according to the present invention, but 96,000 Nmm in the conventional example, and the change of the rotational torque generated at the same rotational angle is suppressed to about 1/1000. I understand that.

  Therefore, according to the nail driver 1 of the present embodiment, the bumper holder 65 and the adjuster 66 via the O-ring 67 are compared with the frictional force generated when the bumper holder 65 and the adjuster 66 which is a screw member are in direct contact. Since the frictional force applied between the bumper holder 65 and the bumper holder 65 is small, the rotational torque of the adjuster 66 is unlikely to increase, and the operability is not lowered even if a follow-up occurs.

  Further, in the O-ring 67, by using a shape and a material such that the displacement related to the tightening becomes a displacement in the elastic deformation region, the rotating torque does not change excessively in the state where the adjuster 66 is tightened. Operability can be improved.

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 · · Sub-body 24 · · Push lever 24A · · Energizing member 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 (6)

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 bumper disposed on the moving shaft and defining an axial one-side dead center when the plunger collides;
A receiving surface for receiving the bumper, a first screw portion positioned on the anti-bumper side with respect to the receiving surface and having the moving axis direction as a screw advance / retreat direction, and a holder side positioned on the anti-bumper side with respect to the receiving surface A bumper holder having a bearing surface;
A second screw portion that is screwed to the first screw portion; and a screw portion side seating surface that faces the holder side seating surface, and rotates about a movement axis relative to the bumper holder to move the movement shaft of the bumper holder. A screw member that defines a position in a direction;
A driving machine comprising: an elastic body disposed between the holder side seating surface and the screw portion side seating surface. The bumper holder is held by the housing so as to be rotatable in a range of a certain rotation angle around the moving axis,
2. The driving machine according to claim 1, wherein the screw member is held by the housing so as to be rotatable around the moving shaft and not movable in one direction of the moving shaft. The housing is formed with an opening through which a part of the screw member is exposed to the outside,
3. The screw member according to claim 1, wherein an operation portion for rotating the screw member is provided on an outer periphery around the moving shaft, and the operation portion is exposed from the opening. Machine.   The spring constant related to the displacement of the elastic body in the moving axis direction is smaller than the spring constant of each of the bumper holder and the screw member when the holder side seating surface is in contact with the screw part side seating surface. The driving machine according to any one of claims 1 to 3.   The elastic body is in an elastic deformation region in a state where a rotational torque is applied to the screw member so that the holder side seating surface and the screw portion side seating surface are close to each other. The driving machine according to claim 4. The first screw is constituted by a male screw and protrudes from the holder side seating surface toward one end side in the movement axis direction,
6. The striking device according to claim 1, wherein the second screw portion is formed of a female screw, and an opening of the female screw is formed on the screw portion side seating surface. Embedded machine.

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