JP4709022B2 - Driving tool - Google Patents

Description

  The present invention relates to a driving tool for performing a driving work of a driving material on a workpiece.

Conventionally, for example, Patent Document 1 below discloses an electric tucker that performs a driving operation of a driving material such as a needle on a workpiece by using a motor as a power source. In this electric tacker, the hammer for striking the driving material is urged in the striking direction by the spring, and this hammer is driven to the end position against the spring force by the driving force of the motor. The driving force of the motor is cut off at this end position, so that the driving material is hit by the spring force of the spring.
By the way, in this type of driving work tool, there is a demand for a technique for defining the working stroke of the driving work so as to prevent double driving due to the configuration in which a single driving operation of the driving material is continuously repeated. . Therefore, in order to meet such a request, for example, a rotating body that is rotationally driven in conjunction with the driving operation is locked once at the driving standby position by the locking means, and after the locking is released, the rotating body is rotated once. It is possible to adopt a configuration that defines the working stroke of the driving operation by locking the rotating body again at the driving standby position. In such a configuration, it is necessary to facilitate the driving operation by reliably performing the rotating operation of the rotating body used to define the operation stroke of the driving operation.
Japanese Patent Publication No. 7-100306

  Therefore, the present invention has been made in view of the above points, and provides a technique effective in facilitating the driving operation in a driving tool for driving a driving material into a workpiece. Is an issue.

  In order to achieve the above object, the invention described in each claim is configured. In the present invention, typically, various types of operations such as a nailing machine and a tucker are used to drive a workpiece by a driving material by linearly operating an operating member by the elastic force of a coil spring. It is a technique that can be applied to tools.

(First invention of the present invention)
A first invention of the present invention that solves the above-described problem is a driving tool according to claim 1.
This driving work tool of the present invention is a driving work tool for driving a driving material into a workpiece, and includes a coil spring, an operating member, a driving means, a rotating body, a first outer edge, a second outer edge, The first standing wall, the second standing wall, the engaging member, and the conversion mechanism are provided at least.

  The coil spring of the present invention is configured as a coil spring capable of accumulating elastic force. In the case of a compressible coil spring, the elastic force is accumulated by contracting the coil spring, and the elastic force of the coil spring is released by the free extension operation of the coil spring in which the elastic force is accumulated. It will act on the actuating member of the present invention attached to the spring end. The actuating member is configured as a member that applies a driving force to the driving material by operating linearly by a free extension operation of the coil spring in which the elastic force is accumulated. As this “driving material”, a straight rod having a pointed tip and having or not having a cap at the head, U-shaped staples and the like can be used.

  The drive means of the present invention is configured as means for accumulating an elastic force in the coil spring by driving the coil spring. The driving operation of the driving material is performed through the operating member by releasing the coil spring which is driven by the driving means and stores the elastic force. Therefore, this driving means constitutes a driving source for the driving material that applies a driving force to the driving material together with the coil spring. As for the driving of the coil spring by this driving means, the coil spring having a structure in which the elastic force is accumulated by being contracted is driven in the spring compression direction against the elastic force to accumulate the elastic force in the coil spring. This is a typical example. This drive means is constituted by a mechanism including a drive source such as a motor and a compressed air supply device, and a speed reducer driven by the drive force of these drive sources.

  The rotating body of the present invention is configured as a member that rotates in the forward rotation direction against the elastic force of the coil spring as the coil spring is driven by the driving means. The rotating operation of the rotating body is linked with the driving operation of the coil spring by the driving means, and the urging force from the coil spring can reach the rotating body when the driving means is stopped. That is, in the drive stop state of the drive means, the rotating body receives a biasing force in the reverse rotation direction opposite to the normal rotation direction in accordance with the elastic force of the coil spring.

  The 1st outer edge part of this invention is comprised as a site | part extended in the circumferential direction by the 1st distance from the rotation center of the said rotary body in the outer edge of a rotary body. Moreover, the 2nd outer edge part of this invention is comprised as a site | part extended in the circumferential direction by the 2nd distance shorter than a 1st distance connected with the 1st outer edge part in the outer edge of a rotary body.

  The 1st standing wall of this invention is comprised as a site | part standing like a wall between the front end side area | region of a 1st outer edge part, and the rear end side area | region of a 2nd outer edge part regarding the normal rotation direction of a rotary body. Is done. Moreover, the 2nd standing wall of this invention is a site | part standing like a wall between the rear end side area | region of a 1st outer edge part, and the front end side area | region of a 2nd outer edge part regarding the normal rotation direction of a rotary body. Configured as

  The engaging member according to the present invention is configured so that the first outer edge portion passes through the first standing wall from the state engaged with the second outer edge portion in accordance with the rotation operation of the rotating body in the positive rotation direction when the coil spring is driven by the driving means. Moving toward the outer side in the radial direction of the rotating body, sliding on the first outer edge portion, moving toward the inner side in the radial direction of the rotating body toward the second outer edge portion through the second standing wall, By returning to the state of being engaged with the second outer edge portion again, it has a function of defining the working stroke of the driving work. In the driving tool of the present invention, it is necessary to define the working stroke of the driving work because of the configuration in which a single driving operation of the driving material is continuously repeated. The working stroke of the driving work is defined by cooperation with the member. Typically, a cam disk having at least two types of cam diameters can be used as the rotating body, and the locking member is a shaft-like member or lever that engages with the cam surface as the cam disk rotates. A member can be used. Here, the “work stroke” is synonymous with a single work cycle from the start of driving to the completion of driving.

  By the way, when the engagement member of the present invention returns to the state in which the engagement member is again engaged with the second outer edge portion through the first outer edge portion, the engagement member is moved to the front end of the second outer edge portion according to the stop timing of the rotating body. It stops at an arbitrary position between the side region and the rear end side region. That is, the driving start position at the beginning of the driving stroke of the driving operation and the driving end position at the end of the driving stroke of the driving operation change from the front end side region to the rear end side region of the second outer edge portion each time. It becomes. Further, depending on the stop timing of the rotating body, the position before the engagement member returns to the state where it is engaged with the second outer edge again through the first outer edge, that is, from the first outer edge toward the second outer edge. It is assumed that a locked state in which the rotating body is engaged with and stopped at a position in the middle of moving in the radial direction of the rotating body is assumed. In such a locked state, the engaging member rotates in the reverse rotation direction in accordance with the timing when the engaging member moves inward from the first outer edge portion toward the second outer edge portion and the elastic force of the coil spring. It occurs when the timing to operate matches. When such a locked state occurs, the operation of the engagement member returning to the state of being engaged with the second outer edge portion again through the first outer edge portion is restricted, which may hinder smooth driving operation. Therefore, the driving tool according to the present invention adopts a configuration in which the conversion mechanism according to the present invention is mounted on the assumption that such a locked state occurs.

In the conversion mechanism of the present invention, in the process in which the engaging member moves inward in the radial direction of the rotating body toward the second outer edge portion through the second standing wall, the drive unit stops driving in the positive rotation direction of the rotating body. When the rotation operation is stopped, the second standing wall of the rotating body exerts a pressing force that presses the engagement member in the reverse rotation direction according to the elastic force of the coil spring, and the engagement member is applied to the second outer edge portion. It has a function of converting to a force that returns to the engaged state. When the conversion mechanism having such a configuration is used, the timing at which the engaging member moves inward in the radial direction of the rotating body from the first outer edge portion to the second outer edge portion, and the rotating body are reversed according to the elastic force of the coil spring. Even when the timing of the rotational operation in the rotational direction matches, the engagement member is engaged with the second outer edge portion by the pressing force of the engagement member due to the rotational operation of the rotating body in the reverse rotational direction. It is possible to return to
Therefore, according to such a configuration of the driving tool of the first aspect, the smooth operation in which the engagement member returns to the state of being engaged with the second outer edge portion again through the first outer edge portion can be performed by the conversion mechanism. Thus, a smooth driving operation can be performed.

(Second invention of the present invention)
A second invention of the present invention that solves the above problem is a driving tool according to claim 2.
According to the driving tool of the present invention, in the configuration according to claim 1, in the process in which the engaging member moves inward in the radial direction of the rotating body toward the second outer edge portion through the second standing wall, the driving means When the rotation operation of the rotating body in the positive rotation direction is stopped by stopping the driving, the engaging member and the second standing wall come into contact with each other. And the conversion mechanism in this invention is comprised using the 1st inclined surface and the 2nd inclined surface. The first inclined surface is an inclined surface that is inclined so that a contact portion of the engaging member with the second standing wall expands toward the second standing wall side toward the distal end side of the engaging member. Composed. The second inclined surface is configured as an inclined surface that is inclined so that a contact portion of the second standing wall with the engaging member is parallel to the first inclined surface at the time of the contact. Thereby, the conversion mechanism uses the sliding action of the first inclined surface and the second inclined surface when the engaging member is pressed in the reverse rotation direction via the second standing wall of the rotating body. The engaging member has a function of moving inward in the radial direction of the rotating body toward the second outer edge.
Therefore, according to such a configuration of the driving tool of the second aspect, the conversion mechanism is realized by a simple configuration using the first inclined surface on the engaging member side and the second inclined surface on the rotating body side. It becomes possible.

  According to the present invention, in the driving tool for driving a driving material such as a nail into the workpiece, in particular, the engagement member passes through the second standing wall toward the second outer edge portion in the radial direction of the rotating body. When the rotation of the rotating body in the forward rotation direction is stopped by stopping the driving of the driving means in the process of moving to the position, the second standing wall of the rotating body reverses the engaging member according to the elastic force of the coil spring. By mounting a conversion mechanism that converts the pressing force that presses in the rotation direction into a force that returns the engagement member to a state in which the engagement member is engaged with the second outer edge portion, the engagement member is moved from the first outer edge portion to the second position. A smooth operation to return to the state of being engaged with the outer edge portion is permitted through this conversion mechanism, and thus it is possible to perform a smooth driving operation.

  Hereinafter, embodiments of the present invention will be described in detail with reference to FIGS. This embodiment will be described using a rechargeable pin tacker as an example of the “driving work tool” of the present invention. FIG. 1 is a side sectional view showing an overall configuration of rechargeable pin tacker 100 according to the present embodiment, and FIG. 2 is a sectional view based on the AA line in rechargeable pin tacker 100 of FIG. FIG. 3 is an enlarged cross-sectional view showing the configuration of the main part of the rechargeable pin tacker 100 in FIG.

  As shown in FIG. 1, the rechargeable pin tacker 100 according to the present embodiment generally includes a main body 101 that forms an outer shell of the rechargeable pin tacker 100, a battery case 109 in which a battery is accommodated, It is mainly composed of a magazine 111 loaded with pins as driving materials to be driven into the workpiece.

The main body 101 includes a motor housing 103 that houses a drive motor 113, a gear housing 105 that houses a driving mechanism 117 and a hammer drive mechanism 119, and a hand grip 107 held by an operator.
A hand grip 107 is disposed above the motor housing 103, a gear housing 105 is disposed at one horizontal end (the right side in FIG. 1) of the motor housing 103 and the hand grip 107, and a battery case 109 is disposed at the other horizontal end. Be placed. A magazine 111 is disposed below the motor housing 103 and the gear housing 105. The magazine 111 is configured to supply the pins to be driven to the lower end portion of the gear housing 105, that is, the pin injection portion 112 connected to the distal end portion of the main body portion 101.

  As shown in FIG. 3, the driving mechanism 117 includes a rod-shaped slide guide 121 that extends linearly in the vertical direction and has an upper end portion and a lower end portion fixed to the gear housing 105, and a cylindrical shape on the slide guide 121. A hammer 125 mounted so as to move up and down via a slider 123, a compression coil spring 127 as a means for applying a resilient force to the hammer 125 so as to drive the hammer 125 downward, and the hammer 125 move together. The driving force is applied to the pin supplied to the pin driving port 112a of the injection unit 112, and the driver 129 drives the pin into the workpiece. The hammer 125 and the driver 129 are connected by a connecting pin 131. The hammer 125 has upper and lower engaging protrusions 125a and 125b that are engaged with the upper and lower lift rollers 137 and 139 of the hammer drive mechanism 119 and pushed upward. For convenience, illustration of pins and workpieces is omitted.

  Here, the compression coil spring 127 according to the present embodiment is compressed to accumulate the elastic force, and the compression coil spring 127 in which the elastic force is accumulated freely expands to release the elastic force. The compression coil spring 127 corresponds to the “coil spring” in the present invention. The compression coil spring 127 is also referred to as “compression coil spring”. Further, the hammer 125 and the driver 129 in the present embodiment are actuating members that act linearly by a free extension operation of the compression coil spring 127 in which the elastic force is accumulated, and constitute an “acting member” in the present invention.

  The hammer 125 and the driver 129 are connected by a connecting pin 131. The hammer 125 has an upper engagement protrusion (engagement protrusion 125a in FIGS. 2 and 3) and a lower engagement protrusion (engagement protrusion 125b in FIG. 2). The upper engaging protrusion 125a is configured to engage with the upper lift roller (lift roller 137 in FIG. 2) of the hammer drive mechanism 119 and push it upward. The lower engaging protrusion 125b is configured to be engaged with a lower lift roller (lift roller 139 in FIGS. 2 and 3) of the hammer drive mechanism 119 and pushed upward. The pin as the driving material is in the form of a straight bar with a sharpened tip, and a pin having or not having a shade on the head is used. For convenience, illustration of pins and workpieces is omitted.

  In the present embodiment, the handgrip 107 is provided with a safety lever 143 that prohibits the pulling operation of the trigger 141. The trigger 141 cannot be pulled when the safety lever 143 is placed in the locked position indicated by the solid line in FIG. 1, and when the safety lever 143 is placed in the unlocked position indicated by the phantom line in FIG. 1. Pull operation is possible. The main body 101 is provided with a light 145 (see FIG. 1) for irradiating a pin driving area. When the safety lever 143 is placed in the unlocked position, the light 145 is turned on when the light lighting switch 147 is turned on by the safety lever 143, and when the safety lever 143 is placed in the locked position. The light lighting switch 147 is turned off when it is turned off.

  The rotational output of the drive motor 113 is transmitted as a rotational motion to the hammer drive mechanism 119 via the planetary gear type reduction mechanism 115. The drive motor 113 and the hammer drive mechanism 119 are means having a function of accumulating elastic force in the compression coil spring 127 by driving the compression coil spring 127, and constitute “drive means” in the present invention. As shown in FIGS. 2 and 3, the hammer drive mechanism 119 includes upper and lower gears 133 and 135, which are meshed and engaged with each other and rotated in opposite directions within the vertical plane, and lower gears 133 and 135. The upper and lower lift rollers 137 and 139 (see FIG. 2) that push the hammer 125 upward in accordance with the rotational movement of 135 are mainly configured.

  The gears 133 and 135 are rotatably mounted on a frame 134 disposed in the gear housing 105 via shafts 133a and 135a. The lift rollers 137 and 139 are rotatably mounted via support shafts 137a and 139a at positions eccentric from the rotation centers of the gears 133 and 135, and circularly move around the centers of the gears 133 and 135 as the gears 133 and 135 rotate. That is, it moves in an arc shape. The eccentric amount of the upper lift roller 137 from the support shaft 137a and the eccentric amount of the lower lift roller 139 from the support shaft 139a are set to be equal to each other. The lower gear 135 is meshed with and engaged with a drive gear 115b formed on the output shaft 115a of the speed reduction mechanism 115, and is driven to rotate at a predetermined speed reduction ratio. The gear ratio of the lower gear 135 and the upper gear 133 is set to 1: 1. Further, the lower lift roller 139 and the upper lift roller 137 are arranged to have a phase difference of about 180 degrees. The upper and lower lift rollers 137 and 139 are positioned farthest from each other, that is, the lower lift roller 139 is placed at the lower position of the lower gear 135, and the upper lift roller 137 is placed above the upper gear 133. It will be in the state.

  When the drive motor 113 is energized and the upper and lower gears 133 and 135 are rotated in the direction of the arrows in FIG. 2, the lower lift roller 139 is placed at the bottom dead center position (driving completion position) shown in FIG. The lower part of the hammer 125 engages with the engaging protrusion 125b from below to make a circular motion upward, and the hammer 125 is pushed upward by a vertical component of the circular motion. When the push-up amount of the hammer 125 by the lower lift roller 139 reaches near the maximum, the upper lift roller 137 engages with the engagement protrusion 125a of the upper portion of the hammer 125 from below and circularly moves upward, Push the hammer 125 upward.

  Thus, the hammer 125 is moved upward from the bottom dead center, that is, to the top dead center side via the relay of the upper and lower lift rollers 137 and 139, and the compression coil spring 127 is compressed by the upward movement of the hammer 125. Elasticity is accumulated. Specifically, the hammer 125 is stopped and held at the driving standby position as shown in FIG. Then, by the subsequent pulling operation of the trigger 141, the upper engaging protrusion 125a of the hammer 125 is further transferred from the upper lift roller 137 to the cam 140 in the vicinity of the top dead center. When the driver 129 is pulled upward together with the hammer 125, the pins loaded in the magazine 111 are supplied to the pin insertion port 112a of the injection unit 112, and then the engagement with the cam 140 is released at the same time. The hammer 125 is driven downward by the elastic force of the compression coil spring 127. As a result, the pin supplied to the pin driving port 112a of the injection unit 112 is driven into the workpiece by the driver 129 that descends in the pin driving port 112a. The hammer 125 that has been driven in comes into contact with the stopper 126 to reach the bottom dead center.

  Here, the speed reduction mechanism 115 is equipped with a so-called “reverse rotation prevention mechanism” that prevents reverse rotation in the direction opposite to the direction of rotation (forward rotation) driven by the drive motor 113. . This reverse rotation prevention mechanism of the speed reduction mechanism 115 is shown in FIGS. FIG. 5 shows a view of the ratchet wheel 116 and the leaf spring 118 constituting the reverse rotation prevention mechanism of the speed reduction mechanism 115 of the present embodiment as viewed from the driving mechanism 117 side in FIG. 3, and FIG. A side view of the ratchet wheel 116 and leaf spring 118 in FIG. 5 is shown.

  As shown in FIGS. 5 and 6, in the present embodiment, a disc-shaped claw wheel 116 is provided on the output shaft 115 a of the speed reduction mechanism 115. The claw wheel 116 is provided with a plurality of engaged grooves 116a in a circumferential region (claw surface provided on an outer peripheral portion of the claw wheel 116). Each engaged groove 116a has a standing wall 116b extending in the left-right direction in FIG. 6 and an inclined wall 116c extending in an inclined manner from the bottom of the standing wall 116b. On the other hand, a plate-like leaf spring 118 that is allowed to rotate around the output shaft 115 a with respect to the claw wheel 116 is provided at a position facing the claw surface of the claw wheel 116. The leaf spring 118 is provided with an engaging claw 118a, a first contact piece 118b, and a second contact piece 118c on its outer edge. The engaging claw 118a has a shape extending in the direction along the inclined wall 116c of each engaged groove 116a of the claw wheel 116, and can be engaged with each engaged groove 116a in a pressing manner. . When the engaging claw 118a is engaged with the engaged groove 116a, the claw wheel 116 is rotated in the direction of the arrow 10 in FIG. (It is also referred to as “forward rotation” or “forward rotation”), but the hook wheel 116 rotates in the direction of arrow 12 in FIG. 5 with respect to the leaf spring 118 (also referred to as “reverse rotation” or “reverse rotation”) ) Is prohibited.

  Specifically, when the ratchet wheel 116 rotates forward with respect to the leaf spring 118, the engaging claw 118a is engaged by the sliding movement of the inclined wall 116c of each engaged groove 116a with respect to the engaging claw 118a. The engaged grooves 116a to be joined are sequentially switched along the circumferential region of the ratchet wheel 116, whereby the forward rotation of the ratchet wheel 116 is allowed. On the other hand, when the ratchet wheel 116 rotates in the reverse direction with respect to the leaf spring 118, the engaging claw 118a hits a predetermined engaged groove 116a, that is, a standing wall 116b of the plurality of engaged grooves 116a. It is configured to be locked by the engaged groove 116a and maintain the locked state, and thereby the reverse rotation of the ratchet wheel 116 is prohibited.

  In the configuration shown in FIG. 5, the case where the rotation center of the leaf spring 118 matches the rotation center of the claw wheel 116 is described. However, in the present invention, the rotation center of the leaf spring 118 and the rotation of the claw wheel 116 are described. The center positions may coincide with each other or may be arranged at positions shifted from each other. Further, in the configuration shown in FIG. 5, the case where a plurality of engaged grooves 116 a are provided in the circumferential region among the portions of the claw wheel 116 is described, but in the present invention, the arc surface of the claw wheel 116 is described. A member having an engaging claw corresponding to the engaged groove may be used instead of the leaf spring 118 by providing an engaged groove corresponding to the engaged groove 116a on the outer peripheral portion of the plate.

  By the way, when the ratchet wheel 116 rotates forward around the output shaft 115a as the drive motor 113 is driven, it is between the engaging claw 118a and the engaged groove 116a (inclined wall 116c) that are engaged with each other. Due to the frictional force, the leaf spring 118 is dragged in the same direction as the claw wheel 116 and the accompanying rotation occurs. Therefore, in the present embodiment, a configuration is adopted in which the leaf spring 118 is provided with a first abutting piece 118b that can abut against the first abutted wall 105a on the gear housing 105 side. With this configuration, the leaf spring 118 rotates about the output shaft 115a in the direction of the arrow 10 in FIG. 5, and the first contact piece 118b contacts the first contacted wall 105a. At the stop position (solid line position in FIG. 5), further forward rotation is prohibited.

  On the other hand, regarding the reverse rotation of the claw wheel 116, when the leaf spring 118 tries to rotate in the same direction as the claw wheel 116 due to the engagement force between the engagement claw 118a and the engaged groove 116a, the second rotation is applied. At the second stop position (the phantom line position in FIG. 5) where the contact piece 118c is in contact with the second contacted wall 105b on the gear housing 105 side, further reverse rotation is prohibited. .

  In short, the leaf spring 118 of the present embodiment includes the first stop position where the first contact piece 118b contacts the first contacted wall 105a, and the second contact piece 118c the second contacted wall. Rotation is enabled by a predetermined amount of play (clearance 106 having a size d1 in FIG. 5) between the second stop position in contact with 105b. The clearance 106 and a clearance 179 described later are also referred to as “gap” or “gap”. As a result, the reverse rotation of the pinion wheel 116 in the direction of the arrow 12 with respect to the leaf spring 118 is prohibited, but the reverse rotation of the leaf spring 118 itself from the second stop position to the first stop position is allowed. Therefore, as a result, the ratchet wheel 116 is integrated with the leaf spring 118 to allow reverse rotation.

  Next, the configuration of the operating device 160 for operating energization driving and energization stop of the drive motor 113 according to the present embodiment will be described with reference to FIG. The operation device 160 includes a trigger switch 163 that is turned on by a pulling operation by a user, an internal switch 161 that is turned on in conjunction with a pulling operation of the trigger switch 163, and an on state. It is mainly composed of a cam disk 177 for controlling the subsequent ON state or OFF state of the internal switch 161.

  The trigger switch 163 is arranged on the handgrip 107 and is energized by an energizing spring (not shown) in an off state in which energization driving of the drive motor 113 is prohibited at all times. The first switch 148 (see FIGS. 1 and 3) that is turned on to allow the drive motor 113 to be energized by the pulling operation of the trigger 141, and the swing that interlocks the pulling operation of the trigger 141 with the internal switch 161. It is mainly composed of an arm (not shown).

  The internal switch 161 includes a cam block 171 that moves linearly in conjunction with the pulling operation of the trigger 141, and a switch arm that rotates around the support shaft (support shaft 172a in FIG. 3) by the cam block 171. The switch arm 172) in FIG. 3 and the second switch 173 that is turned on to allow the drive motor 113 to be energized by the rotation of the switch arm are mainly configured. The cam block 171 is attached to the frame 134 so that it can move linearly in the same direction as the pulling operation direction of the trigger 141. The cam block 171 is formed in a longitudinal shape (bar shape), and a first inclined surface 171b is provided at the tip portion 171a. The first inclined surface 171b of the cam block 171 is configured as an inclined surface that is inclined so as to expand toward the second standing wall (second standing wall 178e), which will be described later, toward the tip of the cam block 171. The The cam block 171 corresponds to the “engagement member” in the present invention, and the first inclined surface 171b of the cam block 171 corresponds to the “first inclined surface” in the present invention.

  The cam disk 177 is mounted so as to rotate integrally with the upper gear 133 in the aforementioned hammer drive mechanism 119 (see FIG. 3). The cam disk 177 rotates in the forward rotation direction against the elastic force of the compression coil spring 127 as the compression coil spring 127 is driven in the spring compression direction by the drive motor 113 and the hammer drive mechanism 119. And corresponds to the “rotating body” in the present invention. Therefore, in the present embodiment, the rotation direction of the cam disk 177 that rotates as the compression coil spring 127 is driven in the spring compression direction by the drive motor 113 and the hammer drive mechanism 119 is defined as the positive rotation direction (predetermined rotation direction). The rotation direction opposite to the normal rotation direction is defined as the reverse rotation direction (rotation direction opposite to the predetermined rotation direction). The cam disk 177 has a circumferential surface formed on the outer edge thereof as a cam surface 178, and the cam surface 178 is disposed so as to face the tip 171a of the cam block 171. The cam surface 178 of the cam disk 177 includes at least a scooping inclined region 178a, a large diameter region 178b, a small diameter region 178c, a first standing wall 178d, and a second standing wall 178e.

  A scooping inclined region 178a formed on the cam surface 178 of the cam disk 177 is located between the large-diameter region 178b and the small-diameter region 178c, and is formed by a slope extending linearly from the small-diameter region 178c toward the large-diameter region 178b. Is done. This scooping inclined region 178a engages with the tip 171a of the cam block 171 moved in the closing direction in which the second switch 173 is turned on in conjunction with the pulling operation of the trigger 141 in the circumferential direction of the cam disk 177. The cam block 171 is further moved in the closing direction, thereby releasing the interlock between the cam block 171 and the trigger 141 side.

Both the large diameter region 178 b and the small diameter region 178 c formed on the cam surface 178 of the cam disk 177 are configured as circular arc surfaces centered on the rotation axis of the cam disk 177.
The large-diameter region 178b is a region having a relatively large distance from the rotation center of the cam disk 177, and moves relatively while maintaining the engagement between the scooping inclined region 178a and the tip portion 171a of the cam block 171. Thus, the second switch 173 is configured as an area for maintaining the ON state. On the other hand, the small-diameter region 178c is a region having a relatively small distance from the rotation center of the cam disk 177, disengages the large-diameter region 178b from the tip portion 171a of the cam block 171, and the second switch It is configured as an area that permits the return to the OFF state of 173. In particular, in the present embodiment, as shown in FIG. 7, the small-diameter region 178 c occupies a range exceeding 90 degrees on the circumference of the cam disk 177. This is set to be used as a braking or inertial operation region of the drive motor 113 after the energization of the drive motor 113 is stopped due to the return of the second switch 173 to the off state. That is, the small diameter region 178c is configured to include a braking or inertial operation region.
The large diameter region 178b here corresponds to the “first outer edge portion extending in the circumferential direction at a first distance from the rotation center of the rotating body” in the present invention, and the small diameter region 178c here is the present invention. Corresponds to “a second outer edge portion connected to the first outer edge portion and extending in the circumferential direction at a second distance shorter than the first distance”.

  The first standing wall 178d formed on the cam surface 178 of the cam disk 177 is configured as a standing wall formed at the boundary between the small diameter region 178c and the scooping inclined region 178a. The first standing wall 178d abuts against (abuts against) the side surface of the distal end 171a of the cam block 171 so that the rotation (overrun) beyond the specified position of the cam disk 177 is restricted. In this cam disk 177, the front end 171a of the cam block 171 is in contact with the first standing wall 178d while engaging with the small diameter region 178c at the end of the small diameter region 178c on the side of the narrow inclined region 178a. A contact or close position is defined as a driving standby position. Here, the first standing wall 178d is a portion standing in a wall shape between the front end side region of the large diameter region 178b and the rear end side region of the small diameter region 178c in the positive rotation direction of the cam disk 177. Yes, and corresponds to the “first standing wall” in the present invention.

  The second upright wall 178e formed on the cam surface 178 of the cam disk 177 has a rear end side area and a small diameter area in the large diameter area 178b with respect to the positive rotation direction (counterclockwise in FIG. 7) of the cam disk 177. It is configured as a standing wall formed at the boundary with the front end side region of 178c. The second upright wall 178e has a second inclined surface 178f inclined so as to be parallel to the first inclined surface 171b when the second upright wall 178e contacts the first inclined surface 171b of the cam block 171. It is set as the structure provided. Here, the second standing wall 178e corresponds to the “second standing wall” in the present invention. In addition, the second inclined surface 178f of the second standing wall 178e is wall-shaped between the rear end side region of the large diameter region 178b and the front end side region of the small diameter region 178c with respect to the positive rotation direction of the cam disk 177. It corresponds to the “second inclined surface” in the present invention.

  The driving motor 113 includes a first motor driving switch 148 that is directly operated by a trigger 141 and a second motor driving switch 173 that is operated by an internal switch 161 that is interlocked with the pulling operation of the trigger 141. The energization drive is performed when the switch is turned on, and the power is cut off when either the first switch 148 or the second switch 173 is switched off. When the drive motor 113 is energized, the hammer drive mechanism 119 is driven via the speed reduction mechanism 115 as described above. The hammer drive mechanism 119 compresses the hammer 125 while compressing the compression coil spring 127 in the spring compression direction. Push up from bottom dead center to top dead center. Then, the hammer 125 that has been stopped and held at the driving standby position as shown in FIG. 4 and has reached the top dead center by the pulling operation of the trigger 141 is driven downward by the elastic force of the compression coil spring 127. In this driving operation by the hammer 125, the hammer 125 returns to the driving standby position again from the driving standby position shown in FIG. 4 through the bottom dead center position shown in FIG. Is also defined).

  Further, as described above, when the first driving operation by the hammer 125 is performed by pulling the trigger 141, the second switch 173 operated by the internal switch 161 performs the first pin driving operation. Even when the pulling operation of the trigger 141 is maintained as it is when the operation is completed, the operation is turned off. That is, when the first pin driving operation by the hammer 125 is completed, the drive motor 113 is de-energized at that time, and even if the pulling operation of the trigger 141 is maintained, the configuration cannot be shifted to the second pin driving operation. Has been. This prevents so-called double hitting of the pin. In addition, when the drive operation of the trigger 141 is released and the drive operation of the trigger 141 is released before the pin driving operation by the hammer 125 is completed after the drive motor 113 is energized, the trigger 141 is operated directly. When the first switch 148 is turned off, the energization of the drive motor 113 is cut off, and the pin driving operation by the hammer 125 can be interrupted.

  Here, the operation of the reverse rotation prevention mechanism of the speed reduction mechanism 115 will be described with reference to FIGS. In FIG. 8, when the working stroke of the driving operation is completed, a contact state is formed in which the tip portion 171a of the cam block 171 is engaged with the first standing wall 178d of the cam disk 177 while engaging the small diameter region 178c. Is shown. Further, FIG. 9 shows a contact release state in which the front end portion 171a of the cam block 171 is engaged with the small diameter region 178c and the contact between the front end portion 171a and the first standing wall 178d of the cam disk 177 is released. It shows how it was done.

  In the state shown in FIG. 8, immediately after the operation stroke of the driving operation is completed, the inertia force in the positive rotation direction (the direction of arrow 30 in FIG. 8) acts on the cam disk 177, and the tip portion 171a of the cam block 171 An abutting state (also referred to as “contact state”) that abuts against the first standing wall 178d of the cam disk 177 is formed. The inertial force acting on the cam disk 177 is, in order from the drive motor 113 side, the rotational force of the output shaft 115a in the direction of arrow 10, the rotational force of the lower gear 135 in the direction of arrow 20, and the upper gear 133. It is transmitted as a rotational force in the direction of arrow 30. On the other hand, immediately after the operation stroke of the driving operation is finished, the leaf spring 118 is engaged with the engagement groove 116a of the claw wheel 116 by the engagement claw 118a, and the engagement state is formed. A state is formed in which the first contact piece 118b is in contact with the first contacted wall 105a on the gear housing 105 side. As a result, the leaf spring 118 is prevented from being dragged in the same direction as the claw wheel 116 and causing accompanying rotation.

  By the way, when the state where the tip 171a of the cam block 171 abuts against the first standing wall 178d of the cam disk 177 matches the state where the claw wheel 116 and the leaf spring 118 are engaged, It is assumed that a locked state is formed in which the operation of block 171 is locked. When such a locked state is formed, even if the trigger 141 is pulled, the end of the cam block 171 cannot be released from the contact with the first standing wall 178d, and the cam block 171 is pulled up. This will cause problems that are not possible.

  Therefore, in the present embodiment, the distal end portion 171a of the cam block 171 abuts against the first standing wall 178d of the cam disk 177 and is engaged with each other even when the claw wheel 116 and the leaf spring 118 are engaged. A predetermined amount of reverse rotation of the claw wheel 116 and the leaf spring 118 in the combined state is allowed. Specifically, as described above, the leaf spring 118 includes the first stop position where the first contact piece 118b contacts the first contacted wall 105a, and the second contact piece 118c the second contacted piece 118c. Rotation is enabled by a predetermined amount of play (clearance 106 having a size d1 in FIG. 8) between the second stop position in contact with the contact wall 105b. At this time, the elastic force of the compression coil spring 127 acts on the ratchet wheel 116 via the speed reduction mechanism 115 and tries to rotate the pinion wheel 116 in the reverse rotation direction. Therefore, the ratchet wheel 116 to which the elastic force of the compression coil spring 127 has been transmitted is integrated with the leaf spring 118 in which the engagement claw 118a is locked in the predetermined engaged groove 116a. When the leaf spring 118 rotates counterclockwise by a distance corresponding to the size d1 of the clearance 106 and the leaf spring 118 rotates around the output shaft 115a in the direction of the arrow 12 in FIG. 9 and moves to the second stop position, the second When the contact piece 118c contacts the second contacted wall 105b, further reverse rotation is prohibited.

  In the process in which the claw wheel 116 is integrated with the leaf spring 118 and reversely rotates by a distance corresponding to the size d1 of the clearance 106, the cam disk 177 also rotates in the reverse direction, as shown in FIG. In addition, the front end 171a of the cam block 171 is separated from the first standing wall 178d of the cam disk 177 by a predetermined distance (a clearance 179 of size d2), and the abutment of each other is released (contact release state) ) Is formed. That is, since the clearance between the second contact piece 118c of the leaf spring 118 and the second contacted wall 105b is eliminated, this time, the front end 171a of the cam block 171 and the first standing wall 178d of the cam disk 177 are removed. A clearance 179 having a size d2 is generated between the two. That is, in the present embodiment, the clearance 106 between the second abutting piece 118c of the leaf spring 118 and the second abutted wall 105b defines the amount of rotation in the reverse rotation of the cam disk 177. Yes.

  The rotational force of the cam disk 177 in the reverse rotation is sequentially transmitted from the compression coil spring 127 to the engagement protrusion 125a at the upper part of the hammer 125 and then to the support shaft 137a of the upper lift roller 137. As described above, the clearance 179 having the size d2 is formed between the front end portion 171a of the cam block 171 and the first standing wall 178d of the cam disk 177, so that the first standing wall 178d is engaged. Since the contact is avoided and the operation lock of the cam block 171 is prevented, the trigger 141 can be pulled smoothly.

  When the driving operation is started from the state shown in FIG. 9, the cam block 171 operates in conjunction with the pulling operation of the trigger (trigger 141 in FIG. 3), and is pulled up in the direction of arrow 40 in FIG. It is done. The direction of the arrow 40 corresponds to “the outer side in the radial direction of the rotating body” in the present invention. As described above, in the course of the pulling operation of the trigger 141, the drive motor 113 is energized and the cam disk 177 rotates in the forward rotation direction. Therefore, the cam pulled up in the direction of the arrow 40 in FIG. The tip 171a of the block 171 moves relative to the scooping inclined region 178a and then climbs onto the large-diameter region 178b, and the cam disk 177 further rotates in the forward rotation direction as shown in FIG. And move relative to each other while engaging with the large diameter region 178b. FIG. 10 shows a state in which the tip 171a of the cam block 171 is engaged with the large diameter region 178b.

  From this state shown in FIG. 10, the cam disk 177 is further rotated in the forward rotation direction so that the front end portion 171a of the cam block 171 moves from the rear end region of the large diameter region 178b of the cam disc 177 to the second standing wall 178e. And reaches the small-diameter region 178c. At this time, the cam block 171 moves downward in the direction of the arrow 42 in FIG. 11, whereby the second switch 173 is returned to the OFF state, and energization to the drive motor 113 is stopped. The direction of the arrow 42 corresponds to the “rotary body radial direction inside” in the present invention. Thereafter, the drive motor 113 is stopped after being braked and continuously rotated by inertia against the elastic force of the compression coil spring 127. As a result, the distal end portion 171a of the cam block 171 moves relative to the small-diameter region 178c and then moves to the first standing wall 178d of the cam disk 177 at the driving standby position as shown in FIG. 8 or FIG. A bumped state or a state close to the first standing wall 178d is formed. Although details will be described later, depending on the stop timing of the cam disk 177, the second standing erection is performed with the tip 171a of the cam block 171 engaged with the small diameter region 178c at the driving standby position as shown in FIG. A state where it abuts against the wall 178e or a state close to the second standing wall 178e is formed. This driving standby position is a driving start position at the beginning of the working stroke of the driving work and a driving end position at the end of the working stroke of the driving work.

  However, in the process in which the front end 171a of the cam block 171 reaches the small diameter region 178c from the rear end region of the large diameter region 178b of the cam disk 177 through the second standing wall 178e, the cam disk is stopped by energization of the drive motor 113. When the rotation operation in the forward rotation direction of 177 is stopped, it is assumed that the downward movement of the cam block 171 in the direction of the arrow 42 in FIG. 11 is hindered. Here, FIG. 11 shows a state in which the front end portion 171a of the cam block 171 reaches the small diameter region 178c from the rear end region of the large diameter region 178b of the cam disk 177 through the second standing wall 178e. . Specifically, in the positional relationship between the cam block 171 and the cam disk 177 as shown in FIG. 11, when the rotation of the cam disk 177 in the normal rotation direction is stopped, the cam caused by the elastic force of the compression coil spring 127 is used. The movement between the disc block 177 and the cam block 171 is locked in a biting manner by the rotational movement in the reverse rotation direction, and a state where the cam block 171 is not completely lowered until it comes into contact with the small diameter region 178c is formed. Become. In such a locked state, the cam block 171 moves in the reverse rotation direction in accordance with the timing when the cam block 171 moves radially inward from the large diameter region 178b toward the small diameter region 178c and the elastic force of the compression coil spring 127. It can occur when the timing of In such a locked state, energization of the drive motor 113 is stopped, and a swing arm (not shown) that interlocks the pulling operation of the trigger 141 with the internal switch 161 cannot engage the cam block 171, It is in a halfway state in which the pulling operation 141 is impossible.

  Therefore, the rechargeable pin tacker 100 of the present embodiment is equipped with the “conversion mechanism” according to the present invention, assuming the occurrence of such a phenomenon. This conversion mechanism is configured by using the first inclined surface 171b of the cam block 171 and the second standing wall 178e (second inclined surface 178f) of the cam disk 177 as described above. According to this conversion mechanism, even when the cam disk 177 is stopped in the forward rotation direction in the positional relationship between the cam block 171 and the cam disk 177 as shown in FIG. The cam block 171 is moved to the small diameter region 178c by using the sliding action of the first inclined surface 171b and the second inclined surface 178f when pressed in the reverse rotation direction via the second standing wall 178e of the disk 177. The cam disk 177 can be moved inward in the radial direction. That is, the conversion mechanism in the present embodiment is configured so that the second standing wall 178e of the cam disk 177 pushes the cam block 171 in the reverse rotation direction until the cam block 171 contacts the small diameter region 178c. It has a function to convert to a returning force.

  Thus, with respect to the positional relationship between the cam block 171 and the cam disk 177, a state as shown in FIG. 12 can be formed. FIG. 12 shows a state in which the leading end portion 171a of the cam block 171 reaches the small diameter region 178c from the rear end region of the large diameter region 178b of the cam disk 177 through the second standing wall 178e. The state shown in FIG. 12 is a state in which the cam block 171 is engaged with the small diameter region 178c and abuts against the second standing wall 178e. The position of the cam block 171 is shown in FIG. 8 or FIG. The driving standby position (second driving standby position) is different from the driving standby position (first driving standby position). Similarly to the first driving standby position shown in FIG. 8 or FIG. 9, the second driving standby position shown in FIG. 12 includes the driving start position at the beginning of the driving stroke and the working stroke of the driving work. It can be the last driving end position. That is, in the present embodiment, the cam disk 177 stops at an arbitrary position between the front end side region and the rear end side region of the small diameter region 178c according to the stop timing of the cam disk 177, and the front end side region (second standing region) of the small diameter region 178c. The driving standby position of the cam block 171 can be formed at an arbitrary position between the region on the installation wall 178e side and the rear end region (region on the first standing wall 178d side).

  In the state shown in FIG. 12, since energization to the drive motor 113 is stopped and the trigger 141 can be pulled, the driving operation can be started from this state. In this case, the cam block 171 operates in conjunction with the pulling operation of the trigger 141 and is pulled up in the direction of the arrow 40 in FIG. In the course of this pulling operation of the trigger 141, the drive motor 113 is energized and the cam disk 177 rotates in the forward rotation direction, so that the tip of the cam block 171 pulled up in the direction of arrow 40 in FIG. 171a moves relative to the scooping inclined region 178a and then climbs onto the large diameter region 178b, and the cam disk 177 further rotates in the positive rotation direction, as shown in FIG. And move relative to each other. Due to the further rotation of the cam disk 177 in the forward rotation direction, the leading end 171a of the cam block 171 reaches the small diameter area 178c from the rear end area of the large diameter area 178b of the cam disk 177 through the second standing wall 178e. .

  As described above, according to the rechargeable pin tacker 100 of the present embodiment, the first inclined surface 171b of the cam block 171 and the second standing wall 178e (second inclined surface 178f) of the cam disk 177 are used. By mounting the configured conversion mechanism, a smooth operation in which the cam block 171 returns to the state in which the cam block 171 is engaged with the small diameter region 178c again through the large diameter region 178b is permitted. It becomes possible to carry out. In particular, the conversion mechanism can be realized by a simple configuration using the first inclined surface 171b on the cam block 171 side and the second inclined surface 178f on the cam disk 177 side.

(Other embodiments)
Note that the present invention is not limited to the above embodiment, and various application examples and modification examples based on the present embodiment can be conceived. For example, the following embodiments to which this embodiment is applied can be implemented.

  In the above-described embodiment, the case where the conversion mechanism is configured using the first inclined surface 171b on the cam block 171 side and the second inclined surface 178f on the cam disk 177 side has been described. The configuration can be appropriately changed as necessary. For example, an inclined surface corresponding to the first inclined surface 171b or the second inclined surface 178f is formed between the cam block 171 and the cam disk 177, and is constituted by a member separate from the cam block 171 and the cam disk 177. You can also

  Further, in the present embodiment described above, a rechargeable pin tacker is described as an example of a driving tool, but the present invention is not limited to the configuration of the rechargeable pin tacker, The present invention can be applied to the configuration of an air-driven pin tacker and the configuration of a rechargeable, AC-driven, and air-driven nailer.

It is a sectional side view which shows the whole structure of the rechargeable pin tacker 100 which concerns on this Embodiment. It is sectional drawing based on the AA line in the rechargeable pin tacker 100 of FIG. 1, and shows the state in which the hammer 125 is at the bottom dead center position. It is an expanded sectional view which shows the structure of the principal part of the rechargeable pin tacker 100 in FIG. It is sectional drawing based on the AA line in the rechargeable pin tacker 100 of FIG. 1, and shows a state where the hammer 125 is in the driving standby position. It is the figure which looked at the pinion wheel 116 and the leaf spring 118 which comprise the reverse rotation prevention mechanism of the deceleration mechanism 115 of this Embodiment from the driving mechanism 117 side in FIG. FIG. 6 is a side view of the ratchet wheel 116 and the leaf spring 118 in FIG. 5. It is a figure which shows the structure of the operating device 160 which operates the energization drive of the drive motor 113 of this Embodiment, and an energization stop. The figure which shows a mode when the operation | work stroke | stroke of a driving | operation driving | operation is complete | finished and the contact state which contact | abutted against the 1st standing wall 178d of the cam disk 177 was formed, engaging the front-end | tip part 171a of the cam block 171. It is. A state is shown in which the abutting release state in which the abutting between the leading end 171a and the first standing wall 178d of the cam disk 177 is released while the leading end 171a of the cam block 171 is engaged with the small diameter region 178c is formed. FIG. It is a figure which shows a mode when the front-end | tip part 171a of the cam block 171 engages with the large diameter area | region 178b. It is a figure which shows the mode in the middle of the front-end | tip part 171a of the cam block 171 reaching the small diameter area | region 178c via the 2nd standing wall 178e from the rear-end area | region of the large diameter area | region 178b of the cam disk 177. It is a figure which shows a mode that the front-end | tip part 171a of the cam block 171 reached the small diameter area | region 178c via the 2nd standing wall 178e from the rear-end area | region of the large diameter area | region 178b of the cam disk 177.

Explanation of symbols

DESCRIPTION OF SYMBOLS 100 Rechargeable pin tacker 101 Main part 103 Motor housing 105 Gear housing 105a First to-be-contacted wall 105b Second to-be-contacted wall 106 Clearance 107 Hand grip 109 Battery case 111 Magazine 112 Injection part 112a Pin insertion port 113 Drive motor 115 Deceleration mechanism 115a Output shaft 115b Drive gear 116 Claw wheel 116a Engagement groove 116b Standing wall 116c Inclined wall 117 Driving mechanism 118 Leaf spring 118a Engaging claw 118b First contact piece 118c Second contact piece 119 Hammer drive mechanism 121 Slide guide 123 Sliding Child 125 Hammer 125a Upper engaging protrusion 125b Lower engaging protrusion 126 Stopper 127 Compression coil spring 129 Driver 131 Connecting pin 133 Upper gear 133a Shaft 134 Frame 135 Lower Gear 135a Shaft 137 Upper lift roller 137a Support shaft 139 Lower lift roller 139a Support shaft 140 Cam 141 Trigger 143 Safety lever 145 Light 147 Light lighting switch 148 First switch 160 Operating device 161 Internal switch 163 Trigger switch 171 Cam block 171a Tip 171b First inclined surface 172 Switch arm 172a Support shaft 173 Second switch 177 Cam disk 178 Cam surface 178a Scooping inclined region 178b Large diameter region 178c Small diameter region 178d First standing wall 178e Second standing wall 178f Second inclination Surface 179 clearance

Claims (2)

A driving tool for driving a driving material into a workpiece,
A coil spring capable of accumulating elasticity,
An actuating member attached to an end of the coil spring and acting linearly by a free extension operation of the coil spring in which an elastic force is accumulated, thereby applying a driving force to the driving material;
Driving means for accumulating an elastic force in the coil spring by driving the coil spring;
A rotating body that rotates in the positive rotation direction against the resilient force of the coil spring as the coil spring is driven by the driving means;
At the outer edge of the rotating body, a first outer edge portion extending in the circumferential direction at a first distance from the rotation center of the rotating body, and a second shorter than the first distance connected to the first outer edge portion. A second outer edge extending circumferentially at a distance of
A first standing wall standing between a front end side region of the first outer edge portion and a rear end side region of the second outer edge portion with respect to the positive rotation direction of the rotating body, and the rear of the first outer edge portion A second standing wall standing between the end side region and the front end side region of the second outer edge;
When the coil spring is driven by the driving means, the rotating body is rotated in the positive rotation direction from the state engaged with the second outer edge to the first outer edge through the first standing wall. After moving to the outer side in the rotating body radial direction, sliding on the first outer edge portion, moving to the inner side in the rotating body radial direction toward the second outer edge portion through the second standing wall, An engagement member that defines the working stroke of the driving operation by returning to the state of being engaged with the second outer edge again,
In the process in which the engagement member moves inward in the radial direction of the rotating body toward the second outer edge through the second standing wall, the rotation of the rotating body in the normal rotation direction is stopped by stopping the driving means. When the second standing wall of the rotating body presses the engagement member in the reverse rotation direction according to the elastic force of the coil spring, the engagement member A conversion mechanism that converts the force to return to the state engaged with the outer edge,
A driving tool characterized by having a configuration comprising: The driving tool according to claim 1,
In the process in which the engagement member moves inward in the radial direction of the rotating body toward the second outer edge through the second standing wall, the rotation of the rotating body in the normal rotation direction is stopped by stopping the driving means. Is stopped, the engagement member and the second standing wall are in contact with each other,
The converting mechanism is inclined such that a contact portion of the engaging member with the second standing wall is inclined toward the second standing wall side toward the distal end side of the engaging member. Using a second inclined surface that is inclined so that a contact portion between one inclined surface and the engaging member on the second standing wall is parallel to the first inclined surface at the time of the contact. Thus, the sliding of the first inclined surface and the second inclined surface when the engaging member is pressed in the reverse rotation direction via the second standing wall of the rotating body is configured. A driving tool for moving the engagement member toward the inner side in the radial direction of the rotating body toward the second outer edge portion using an operation tool.

Images