Driving tool

Abstract

To provide a driving tool that does not easily impair the operability of dials, etc. [Solution] The driving tool 10 has a contact arm 6 that protrudes forward. The rear part 6c of the contact arm 6 is connected to a connecting member 7. An adjustment mechanism 8 screws the rear part 6c of the arm and the connecting member 7 together. The front-to-back position of the contact arm 6 is adjusted by the rotation of the connecting member 7. The adjustment mechanism 8 has a male screw 8a, a female screw 8b, and a radial gap 8c formed between the male screw 8a and the female screw 8b. The male screw 8a is formed on the connecting member 7. The female screw 8b is formed on the contact arm 6. The size of the radial gap 8c is the difference between the peak diameter D1 of the male screw 8a and the root diameter D2 of the female screw 8b, and is 4-10% of the root diameter D2.

Description

Technical Field

[0001] The present disclosure relates to a driving tool for driving driving tools such as nails and staples into wood and the like.

Background Art

[0002] Conventionally, a driving tool that strikes a driving material such as a nail and ejects it from an ejection port is known. Generally, the driving tool has a contact arm provided in front of the ejection port so as to be retractable backward. The rear portion of the contact arm is connected to a connecting member movably attached to the tool body in the front-rear direction. When performing a driving operation, the contact arm is pressed against the material to be driven, and the contact arm is retracted with respect to the tool body. Then, the trigger provided on the tool body is pulled. By performing both the operation of the contact arm and the operation of the trigger, the driving tool ejects the driving tool.

[0003] The driving tool of Patent Document 1 has an adjustment mechanism for adjusting the front-rear position of the contact arm with respect to the ejection port. The adjustment mechanism has an internal thread formed on the contact arm and an external thread formed on the shaft of the connecting member. The connecting member has a dial that can be rotated by the user. By rotating the dial, the shaft rotates together with the dial, and the contact arm moves back and forth with respect to the shaft. Thereby, the front-rear position of the contact arm can be adjusted, and the driving depth of the driving tool can be adjusted.

[0004] In the above configuration, for example, as shown in FIG. 9, the user rotates the dial 101 while pressing it toward the tool body 100. As a result, the dial 101 and the shaft 102 tilt with respect to the tool body 100. As a result, the contact arm 103 may also be pushed by the shaft 102 and tilt in the opposite direction to the shaft 102. Thereby, the external thread 104 and the internal thread 105 are greatly distorted, and the operation load of the dial 101 increases. As a result, the operability of the dial 101 may deteriorate.

Prior Art Documents

Patent Documents

[0005] [Patent Document 1] Patent No. 7107650 [Overview of the project] [Problems that the invention aims to solve]

[0006] Therefore, there has been a need for a driving tool that does not easily impair the operability of dials and other controls. [Means for solving the problem]

[0007] According to one aspect of this disclosure, the driving tool has a contact arm that protrudes forward from the nozzle. The rear of the contact arm is connected to a connecting member. An adjustment mechanism screws the rear of the arm to the connecting member. The forward and backward position of the contact arm is adjusted by the rotation of the connecting member. The adjustment mechanism has a male thread, a female thread, and a radial gap formed between the male and female threads. The male thread is formed on one of the two members, the contact arm and the connecting member. The female thread is formed on the other of the two members. The size of the radial gap is the difference between the crest diameter of the male thread and the root diameter of the female thread, and is 4 to 10% of the root diameter. Here, the crest diameter is, for example, the length of the diameter connecting the peaks of the male thread radially. The root diameter is, for example, the length of the diameter connecting the roots of the female thread radially. Therefore, the radial gap allows for some play in the adjustment mechanism. That is, even if the male and female threads are misaligned or tilted relative to each other due to, for example, the inclination of the connecting member, the male and female threads are less likely to become twisted. This makes it less likely to worsen the operability of the connecting members. [Brief explanation of the drawing]

[0008] [Figure 1] This is a left side view of the driving tool with the left housing removed, according to the first embodiment of this disclosure. [Figure 2] This is a cross-sectional view taken along line II-II in Figure 1. [Figure 3] This is a perspective view of the adjustment mechanism from the front. [Figure 4] This is a perspective view of the adjustment mechanism from the rear. [Figure 5] Figure 1 is a cross-sectional view along the VV line. [Figure 6] This is a magnified schematic diagram of a male and female screw. [Figure 7] This is a rear-view perspective of the adjustment mechanism according to the second embodiment. [Figure 8] This is a cross-sectional view of the connecting member shown in Figure 7, viewed from above. [Figure 9] This is a cross-sectional view corresponding to Figure 5, which shows a conventional adjustment mechanism. [Modes for carrying out the invention]

[0009] According to other aspects of this disclosure, the male and female threads have the same peak height. Therefore, the male and female threads can easily mesh even with a radial gap.

[0010] According to other aspects of this disclosure, the adjustment mechanism has a female thread formed on the contact arm and a male thread formed on the connecting member. Therefore, the male thread is formed on the rotating connecting member. Thus, the male thread can be easily provided in accordance with the rotation axis of the connecting member.

[0011] According to other aspects of this disclosure, the effective diameter of the male thread is smaller than the effective diameter of the female thread. Therefore, a radial gap between the male and female threads can be easily secured.

[0012] According to other aspects of this disclosure, the connecting member has a dial that is rotated by the user. The outer surface of the dial around its axis is exposed to the outside in a range of 180 degrees or less. Therefore, the user rotates the dial by pushing it from one direction. Even in such cases, the radial clearance can prevent twisting of the male and female threads.

[0013] According to another aspect of the present disclosure, the connecting member has a shaft that extends longitudinally. A male or female thread is formed on the front portion of the shaft. The rear portion of the shaft is supported by the main body support portion of the tool body so as to be movable back and forth. Therefore, an adjustment mechanism screws the rear portion of the arm and the front portion of the shaft together. As a result, the contact arm and the shaft can be arranged side by side in the front-rear direction.

[0014] According to another aspect of the present disclosure, the main body support portion has a hole through which the rear portion of the shaft is inserted. The central axis of the hole is located closer to the tool body side than the central axis of the shaft. Therefore, when the user pushes the connecting member toward the tool body side, the central axis of the hole and the central axis of the shaft are brought closer together. As a result, the connecting member can be rotated with good operability.

[0015] According to another aspect of the present disclosure, the driving tool has a contact portion that abuts against the rear portion of the arm when the dial is pushed from the side where it is exposed to the outside toward the tool body side. Therefore, when the connecting member is operated, the contact portion supports the rear portion of the arm. As a result, the backlash of the adjustment mechanism can be suppressed by the contact portion.

[0016] According to another aspect of the present disclosure, when the dial is pushed from the side where it is exposed to the outside toward the tool body side, the rear portion of the arm does not hit the tool body. In this way, even in a structure where the adjustment mechanism is likely to rattle, it is easy to suppress the jamming of the male and female threads due to the radial clearance.

[0017] According to another aspect of the present disclosure, the rear portion of the arm is formed of a plate-shaped metal, and the female thread is formed as a part of the plate-shaped metal. Thereby, the female thread can be formed at a low cost as a single member with the rear portion of the arm.

[0018] Next, one embodiment of the present disclosure will be described based on FIGS. 1 to 6. As shown in FIG. 1, the driving tool 10 is, for example, a gas spring type that drives a driving tool using gas pressure. In the following description, the driving direction of the driving tool is defined as the forward direction, and the reverse driving direction is defined as the rearward direction. The user holds the driving tool 10 by hand and is located behind the driving tool 10 (the right side of the paper surface in FIG. 1). The vertical and horizontal directions are defined based on the user.

[0019] As shown in FIG. 1, the driving tool 10 has a tool body 1. The tool body 1 has a generally cylindrical housing 1a. As shown in FIG. 2, a cylindrical cylinder 1b extending in the front-rear direction is accommodated in the housing 1a. A piston 1c is accommodated in the cylinder 1b so as to be reciprocable in the front-rear direction. The rear part of the cylinder 1b behind the piston 1c communicates with a pressure accumulation chamber 1d. Compressed gas such as air is enclosed in the pressure accumulation chamber 1d. The gas pressure in the pressure accumulation chamber 1d acts as a thrust force to advance the piston 1c.

[0020] As shown in FIG. 1, a driving nose portion 1e is provided at the front part of the housing 1a. A driving passage 1f is formed inside the driving nose portion 1e. The rear end of the driving passage 1f communicates with the front part of the cylinder 1b. A magazine 2 is coupled to the lower surface side of the driving nose portion 1e. A plurality of driving tools arranged in parallel in the vertical direction are accommodated in the magazine 2. The driving tools are supplied one by one upward from the magazine 2 toward the driving passage 1f.

[0021] As shown in FIG. 1, a contact arm 6 slidable in the front-rear direction is provided on the driving nose portion 1e. The contact arm 6 is biased to advance relative to the driving nose portion 1e (off position). The contact arm 6 retreats along the driving nose portion 1e by being pressed against the workpiece to be driven (on position).

[0022] As shown in FIG. 1, a grip 11 for the user to hold is provided at the lower part of the tool body 1. A trigger 12 that the user pulls with a fingertip is provided on the upper front surface of the grip 11. A trigger switch 13 that switches from an off state to an on state in response to the pulling operation of the trigger 12 is provided inside the grip 11. The pulling operation of the trigger 12 becomes effective when the contact arm 6 is pressed against the workpiece to be driven and moves to the on position.

[0023] As shown in Figure 1, a battery mounting section 14 extending in the front-to-back direction is provided on the lower surface of the grip 11. A battery pack 15 can be detachably attached to the battery mounting section 14. The battery pack 15 can be attached to and detached from the battery mounting section 14 by sliding along the front-to-back direction. The battery pack 15 can be removed from the battery mounting section 14 and repeatedly recharged with a separately prepared charger for reuse. The battery pack 15 can be used as a power source for other power tools. The battery pack 15 operates as a power source that supplies power to the motor 3, etc., which will be described later.

[0024] As shown in Figure 1, a roughly cylindrical drive unit case 16 extending vertically is provided in front of the grip 11. The upper part of the drive unit case 16 is integrally connected to the housing 1a. A connection portion 17 is formed between the drive unit case 16 and the battery mounting portion 14. The grip 11, connection portion 17, drive unit case 16, and housing 1a work together to form a loop shape. A controller 18 is housed in the connection portion 17. The controller 18 mainly controls the drive of the motor 3.

[0025] As shown in Figure 1, a motor 3, which serves as the drive source, is housed inside the drive unit case 16. The motor 3 is housed with its motor axis 3a extending in the vertical direction. The motor 3 is powered by the battery pack 15 and started by pulling the trigger 12. A reduction gear train 3b is provided above the motor 3. A lift mechanism 4 is provided above the reduction gear train 3b. The motor 3, reduction gear train 3b, and lift mechanism 4 are arranged side by side on the motor axis 3a. The rotational output of the motor 3 is reduced by the reduction gear train 3b and output to the lift mechanism 4 (see Figure 2).

[0026] As shown in Figure 2, the lift mechanism 4 is provided on the right side of the driving nose portion 1e. The lift mechanism 4 has a wheel 4a that rotates coaxially with the motor 3. The wheel 4a rotates in the direction of arrow R (counterclockwise in Figure 2). The wheel 4a is restricted from rotating in the direction opposite to arrow R. Six engaging portions 4b are provided along the outer edge of the wheel 4a. The engaging portions 4b are cylindrical shaft members (pins) that extend in the vertical direction.

[0027] As shown in Figure 2, a long driver 5 is attached to the front of the piston 1c. The front part of the driver 5 enters the driving passage 1f. The driver 5 has six engaging parts 5a. Each engaging part 5a protrudes to the right from the right side of the driver 5. Each engaging part 5a is formed in a rack-tooth shape. Each engaging part 5a is provided at a constant interval in the longitudinal direction (front-to-back direction) of the driver 5. Each engaging part 4b of the lift mechanism 4 is sequentially engaged with each engaging part 5a.

[0028] Figure 2 shows the driver 5 set in the standby position before performing the driving operation. One engaged part 5a engages with one engaging part 4b. Specifically, the front rack 5b, which is the furthest forward of the engaged parts 5a, engages with the rear pin 4c, which is located at the rear end in the rotational direction of the wheel 4a among the engaging parts 4b. The rear pin 4c engages with the front rack 5b from the front. The engagement of the rear pin 4c and the restriction of the clockwise rotation of the wheel 4a allow the lift mechanism 4 to support the driver 5 from the front. As a result, the driver 5 and piston 1c are held in the standby position against the gas pressure of the accumulator chamber 1d.

[0029] When using the driving tool 10, the user first grasps the grip 11 in the orientation shown in Figure 1. Then the user presses the contact arm 6 against the material to be driven from behind. This causes the contact arm 6 to retract relative to the driving nose portion 1e. When the user pulls the trigger 12 in this state, the controller 18 rotates the motor 3. The rotation of the motor 3 is then transmitted to the lift mechanism 4 via the reduction gear train 3b.

[0030] Then, as shown in Figure 2, the wheel 4a rotates in the direction of arrow R. The rotation of the wheel 4a causes the rear end pin 4c to move over the front end rack 5b. This disengages the rear end pin 4c and the front end rack 5b from each other. As a result, the piston 1c moves forward due to the gas pressure in the accumulator chamber 1d. This causes the front end of the driver 5 to strike the driving tool loaded in the driving passage 1f.

[0031] The striking tool is ejected from the ejection port 1j located at the front end of the striking nose section 1e. The ejected tool is driven into the material to be struck. The forward-moving piston 1c collides with the damper 1r. This stops the forward movement of the piston 1c and the driver 5. The damper 1r absorbs the impact of the collision with the piston 1c. The damper 1r prevents damage to the piston 1c.

[0032] Even after the piston 1c stops moving forward, the wheel 4a continues to rotate in the direction of arrow R. As a result, the engaging portion 4b located at the front of the wheel 4a's rotation engages with the rearmost engaged portion 5a from the front. As the wheel 4a continues to rotate further, the engaging portion 4b pushes the engaged portion 5a backward. With the rotation of the wheel 4a, each engaging portion 4b pushes each engaged portion 5a in sequence. In this way, the lift mechanism 4 pushes the driver 5 and piston 1c back to their standby positions.

[0033] As shown in Figure 1, the contact arm 6 is a long, metal member extending in the front-rear direction. The front part 6a of the arm is positioned near the nozzle 1j. The middle part 6b of the arm extends in the front-rear direction inside the injection nose section 1e. The rear part 6c of the arm extends to the left from the middle part 6b of the arm, and then bends downward along the left side of the injection nose section 1e.

[0034] As shown in Figures 3 and 4, the rear portion 6c of the arm is formed in a thin plate shape. From the lower rear of the downward-extending rear portion 6c of the arm, a thin circular connecting portion 6d is formed that bends further to the left. The shaft 7a of the connecting member 7 is connected to the connecting portion 6d. The shaft 7a is provided so as to pass through the connecting portion 6d in the front-rear direction. The shaft 7a is a cylindrical member that extends in the front-rear direction along the tool body 1. The rear end of the shaft 7a is inserted into a hole 1m formed in the main body support portion 1k of the tool body 1. The shaft 7a is supported so as to be able to move back and forth and rotate relative to the main body support portion 1k.

[0035] As shown in Figures 5 and 6, a female thread 8b is formed on the connecting portion 6d. A male thread 8a is formed on the outer circumferential surface of the front part of the shaft 7a. The shaft 7a is connected to the connecting portion 6d so as to screw into the female thread 8b. As a result, when the shaft 7a rotates around its axis, the contact arm 6 moves in the front-rear direction relative to the shaft 7a. This adjusts the front-rear position of the contact arm 6 relative to the nozzle 1j when the contact arm 6 is in the ON position (see Figure 1). This front-rear position of the contact arm 6 relative to the nozzle 1j corresponds to the driving depth of the driving tool into the material to be driven. The male thread 8a and female thread 8b constitute the adjustment mechanism 8. The male thread 8a and female thread 8b are formed as metric coarse threads with a nominal diameter of M6.

[0036] As shown in Figure 3, a dial 7b is integrally attached to the outer surface of the shaft 7a. The outer surface of the dial 7b has an uneven shape. The dial 7b is positioned coaxially with the shaft 7a. The dial 7b is rotatable integrally with the shaft 7a. The outer surface of the dial 7b is exposed to the outside (lower left in Figure 3) through a window 1n formed in the housing 1a (exposed portion 7c). The exposed portion 7c of the dial 7b is exposed over an area of ​​less than half of its entire circumference. Specifically, for example, it is exposed over a range of approximately 160 degrees.

[0037] The user rotates the dial 7b by pushing the exposed portion 7c toward the tool body 1. As the dial 7b rotates, the shaft 7a rotates. This adjusts the front-to-back position of the contact arm 6 relative to the shaft 7a, as described above. As shown in Figure 5, the shaft 7a is moved to the right by the force applied by the user pushing the dial 7b. Specifically, with the connection point with the main body support portion 1k as the pivot point, the front part of the shaft 7a is moved closer to the right (towards the tool body 1).

[0038] Therefore, as shown by the dashed line in Figure 6, the male screw 8a is tilted relative to the female screw 8b. However, a radial gap 8c is formed around the entire circumference between the male screw 8a and the female screw 8b, running along the radial direction. This radial gap 8c can absorb the tilt of the male screw 8a. In other words, even when the male screw 8a is tilted, it is less likely to interfere significantly with the female screw 8b. As a result, twisting of the male screw 8a and the female screw 8b is suppressed, and the male screw 8a can rotate smoothly without getting caught on the female screw 8b. In other words, the user can rotate the dial 7b with ease of operation.

[0039] As shown in Figure 6, the radial gap 8c is formed by setting the thread diameter D1 of the male thread 8a to be smaller than the nominal diameter M6 of the male thread 8a. Specifically, the thread diameter D1 is set in the range of 90 to 96% of the 6 mm diameter corresponding to the nominal diameter M6. More preferably, the thread diameter D1 is in the range of 94 to 96% of the nominal diameter M6. In this disclosure, for example, D1 is set to approximately 5.7 mm. This corresponds to approximately 95% of the nominal diameter M6.

[0040] On the other hand, the root diameter D2 of the female thread 8b is made equivalent to the nominal diameter M6 of the female thread 8b. The radial gap 8c is expressed as the difference between the root diameter D2 and the crest diameter D1. Therefore, the radial gap 8c is formed to be in the range of 4 to 10%, more preferably 4 to 6%, of the root diameter D2 of the female thread 8b. The size of the radial gap 8c is adjusted to be smaller than the crest height H1 of the male thread 8a. As a result, even with a radial gap 8c, the engagement between the male thread 8a and the female thread 8b does not completely disengage, and the male thread 8a and the female thread 8b can be properly screwed together.

[0041] As described above, by reducing the thread diameter D1 of the male thread 8a, the effective diameter R1 of the male thread 8a becomes smaller than the effective diameter R2 of the female thread 8b. Also, the dimensions, angles, and pitch of the threads of the male thread 8a are the same as those of a standard metric coarse thread of nominal diameter M6. Therefore, the peak height H1 of the male thread 8a and the peak height H2 of the female thread 8b are the same size.

[0042] The engagement of one thread of the male thread 8a with respect to the female thread 8b is in the range of 3.5 to 5.6% of the nominal diameter M6. This engagement of the male thread 8a is set to be 50 to 80% of the engagement of a normal M6 thread. More preferably, it is desirable to be 70 to 80% of the engagement of a normal M6 thread. In this disclosure, the engagement of the male thread 8a is approximately 0.31 mm. This corresponds to approximately 5.2% of the nominal diameter M6 and approximately 74% of the engagement of a normal M6 thread.

[0043] The rear arm portion 6c and the connecting portion 6d are formed by bending a plate-shaped metal. The female screw 8b is formed as a single component with the rear arm portion 6c and the connecting portion 6d. Therefore, the female screw 8b generally has a configuration in which there is a large variation in positional accuracy and tilt accuracy relative to the male screw 8a. As a result, the male screw 8a may be screwed into the female screw 8b at an angle even in its natural state. However, even with such a configuration, by making the effective diameter R1 of the male screw 8a smaller than the effective diameter R2 of the female screw 8b, the male screw 8a is less likely to interfere with the female screw 8b. Therefore, twisting of the male screw 8a and the female screw 8b can be appropriately suppressed.

[0044] As shown in Figure 4, a bracket 9 is provided behind the dial 7b. The bracket 9 has a dial support portion 9a that supports the rear surface of the dial 7b around its entire circumference. A compression spring 1p is provided between the dial support portion 9a and the main body support portion 1k. The compression spring 1p biases the dial support portion 9a of the bracket 9 forward. As a result, the shaft 7a is biased forward together with the dial 7b. As a result, the contact arm 6 is biased to advance relative to the drive-in nose portion 1e.

[0045] As shown in Figures 4 and 5, the bracket 9 has an arm support portion 9b that protrudes to the right from the dial support portion 9a and then bends forward. The arm support portion 9b supports the rear arm portion 6c of the contact arm 6 from the right. The arm support portion 9b is then supported from the right by the contact portion 2a formed in the magazine 2. Therefore, the rear arm portion 6c is supported from the right by the contact portion 2a of the magazine 2 via the arm support portion 9b. As a result, when the user presses the exposed portion 7c of the dial 7b, the rear arm portion 6c is relatively difficult to move to the right (towards the tool body 1). This makes it easier to prevent twisting of the male screw 8a and the female screw 8b.

[0046] As described above, as shown in Figures 3 and 6, the driving tool 10 has a contact arm 6 that protrudes forward from the injection port 1j. The rear part 6c of the contact arm 6 is connected to a connecting member 7. An adjustment mechanism 8 screws the rear part 6c of the arm to the connecting member 7. The front-to-back position of the contact arm 6 is adjusted by the rotation of the connecting member 7. The adjustment mechanism 8 has a male screw 8a, a female screw 8b, and a radial gap 8c formed between the male screw 8a and the female screw 8b. The male screw 8a is formed on one of the two members, the contact arm 6 and the connecting member 7. The female screw 8b is formed on the other of the two members. The size of the radial gap 8c is the difference between the crest diameter D1 of the male screw 8a and the root diameter D2 of the female screw 8b, and is 4 to 10% of the root diameter D2. Here, the crest diameter D1 is, for example, the length of the diameter connecting the crests of the male screw 8a in the radial direction. The root diameter D2 is, for example, the length of the diameter connecting the roots of the female screw 8b in the radial direction. Therefore, the radial gap 8c allows for some looseness in the adjustment mechanism 8. In other words, even if the male screw 8a and female screw 8b become misaligned or tilted relative to each other due to the tilt of the connecting member 7, for example, the male screw 8a and female screw 8b are less likely to become twisted. This makes it less likely to worsen the operability of the connecting member 7.

[0047] As shown in Figure 6, the male thread 8a and the female thread 8b have the same size thread heights H1 and H2. Therefore, even with a radial gap 8c, the male thread 8a and the female thread 8b can easily engage.

[0048] As shown in Figure 6, the adjustment mechanism 8 has a female thread 8b formed on the contact arm 6 and a male thread 8a formed on the connecting member 7. Therefore, the male thread 8a is formed on the rotating connecting member 7. Thus, the male thread 8a can be easily provided in accordance with the rotation axis of the connecting member 7.

[0049] As shown in Figure 6, the effective diameter R1 of the male thread 8a is smaller than the effective diameter R2 of the female thread 8b. Therefore, a radial gap 8c between the male thread 8a and the female thread 8b can be easily secured.

[0050] As shown in Figure 3, the connecting member 7 has a dial 7b that is rotated by the user. The outer surface of the dial 7b around its axis is exposed to the outside in a range of 180 degrees or less. Therefore, the user rotates the dial 7b by pushing it from one direction. Even in such a case, the radial gap 8c can suppress twisting of the male thread 8a and the female thread 8b.

[0051] As shown in Figures 3 and 4, the connecting member 7 has a shaft 7a that extends forward and backward. A male thread 8a or female thread 8b is formed on the front of the shaft 7a. The rear of the shaft 7a is supported by the main body support portion 1k of the tool body 1 so as to be able to move forward and backward. Therefore, the adjustment mechanism 8 screws the rear of the arm 6c and the front of the shaft 7a into each other. As a result, the contact arm 6 and the shaft 7a can be arranged side by side.

[0052] As shown in Figure 5, the driving tool 10 has a contact portion 2a that contacts the rear arm 6c when the dial 7b is pushed from the side exposed to the outside toward the tool body 1. Therefore, the contact portion 2a supports the rear arm 6c when the connecting member 7 is operated. As a result, the play of the adjustment mechanism 8 is suppressed by the contact portion 2a.

[0053] As shown in Figure 3, the rear portion 6c of the arm is formed from a plate-shaped metal, and the female screw 8b is formed as part of the plate-shaped metal. This allows the female screw 8b to be formed inexpensively as a single component with the rear portion 6c of the arm.

[0054] Next, a second embodiment of the present disclosure will be described with reference to Figures 7 and 8. The driving tool 20 of the second embodiment has a main body support 21 instead of the main body support 1k shown in Figure 4. In the following description, only the parts that differ from the first embodiment will be described in detail.

[0055] Figures 7 and 8 are illustrative diagrams showing the positional relationship between the rear of the shaft 7a and the main support portion 21. As shown in Figure 7, a hole 22 is formed in the main support portion 21 through which the rear of the shaft 7a is inserted. The shaft 7a is assembled so as to be offset to the lower left with respect to the center of the hole 22. Figure 8 shows a cross-sectional view of the shaft 7a and the main support portion 21 from above. In its natural state, the central axis 23 of the hole 22 is positioned to the right (towards the tool body 1).

[0056] Therefore, the shaft 7a is assembled so as to be pressed against the inner circumferential surface on the left side of the hole 22. When the user pushes the dial 7b toward the tool body 1, the central axis 7d of the shaft 7a moves closer to the central axis 23 of the hole 22. This makes it easier for the shaft 7a to rotate relative to the main body support portion 21 when the user pushes and turns the dial 7b. This improves the operability of the dial 7b.

[0057] As shown in Figure 7, the rear arm portion 26 extends forward from the connecting portion 27 along the left side of the driving nose portion 1e. The rear arm portion 26 extends while floating above the driving nose portion 1e. The rear arm portion 26 is supported by the driving nose portion 1e at the end of its forward extension. Therefore, the connecting portion 27 is positioned relatively far from the support portion of the driving nose portion 1e. Also, as shown in Figure 8, the bracket 24 does not have an arm support portion 9b protruding from the dial support portion 25. Therefore, the driving tool 20 does not have a portion that supports the connecting portion 27 from the right. The connecting portion 27 does not come into contact with the tool body 1 when the dial 7b is pushed upward and to the right by the user.

[0058] Therefore, when the user presses the dial 7b, the connecting part 27 tends to shift towards the tool body 1. However, even with such a configuration, the radial gap 8c between the male screw 8a and the female screw 8b can appropriately absorb the misalignment between the male screw 8a and the female screw 8b (see Figure 6). This suppresses twisting of the male screw 8a and the female screw 8b, allowing the dial 7b to be rotated smoothly.

[0059] As described above, as shown in Figures 7 and 8, the main body support portion 21 has a hole 22 through which the rear part of the shaft 7a is inserted. The central axis 23 of the hole 22 is located closer to the tool body 1 than the central axis 7d of the shaft 7a. Therefore, when the user pushes the connecting member 7 toward the tool body 1, the central axis 23 of the hole 22 and the central axis 7d of the shaft 7a are brought closer together. As a result, the connecting member 7 can be rotated with good maneuverability.

[0060] As shown in Figure 8, when the dial 7b is pushed from the side exposed to the outside toward the tool body 1, the rear part of the arm 26 does not come into contact with the tool body 1. Even though the adjustment mechanism 8 has a structure that is prone to rattling, the radial gap 8c helps to suppress twisting of the male thread 8a and the female thread 8b.

[0061] Various modifications can be made to each embodiment described above. For example, a gas spring type was used as an example for the driving tool. Alternatively, the present disclosure may be applied to a driving tool called a mechanical spring type, in which, for example, the driver is moved in the opposite direction of driving by a lift mechanism, and the driver is moved in the driving direction by increasing the spring force of a mechanical compression spring or the like. Furthermore, the present disclosure can be applied to any driving method, such as a flywheel type or a compressed air type connected to a compressor.

[0062] This disclosure illustrates a configuration in which the effective diameter of the male thread is made smaller than the effective diameter of the female thread by forming the thread diameter of the male thread to be smaller in the radial direction than the nominal diameter of the male thread. Alternatively, the effective diameter of the male thread may be made smaller than the effective diameter of the female thread by forming the root diameter of the female thread to be larger in the radial direction than the nominal diameter of the female thread. The male thread may be formed on a contact arm and the female thread may be formed on a connecting member. The peak height of the male thread and the peak height of the female thread may be different. The male and female threads are not limited to a nominal diameter of M6, but may be any diameter as long as the nominal diameter is M12 or less.

[0063] The rear of the arm and the connecting member are located on the left side of the tool body, but may also be located on the right side, above, or at any other arbitrary position. The contact part that supports the rear of the arm may be located on the tool body instead of the magazine. [Explanation of Symbols]

[0064] 10. Driving tools 11 Grips 12 Triggers 13 Trigger Switch 14 Battery mounting section 15 Battery Packs 16 Drive unit case 17 Connection part 18 controllers 1 Tool body 1a Housing 1b Cylinder 1c Piston 1d Accumulator 1e Nose section for driving 1st floor driving passage 1j injection port 1k main body support part 1m hole 1n Window section 1p Compression spring 1r damper 2 Magazines 2a Contact part 3 motors 3a Motor axis 3b Reduction gear train 4. Lift mechanism 4a Wheel 4b Engagement part 4c rear end pin 5 Drivers 5a Engaged part 5b Front end rack 6 Contact Arms 6a Front of the arm 6b Middle part of the arm 6c Rear of the arm 6d connection part 7 Connecting members 7a shaft 7b Dial 7c Exposed part 7d center axis 8 Adjustment mechanism 8a Male screw 8b Female thread 8c radial clearance 9 brackets 9a Dial support part 9b Arm support section 20 driving tools 21 Main body support part 22 holes 23 Central axis 24 brackets 25 Dial support part 26 Rear of the arm 27 Connecting part 100 Tool body 101 Dial 102 Shaft 103 Contact Arm 104 Male screw 105 Female thread R1 Effective diameter R2 Effective diameter H1 Pointed mountain height H2 Pointed Mountain Height D1 Mountain Diameter D2 Valley diameter

Claims

1. It is a driving tool, A contact arm protruding forward from the nozzle, A connecting member connected to the rear part of the contact arm, The rear portion of the arm and the connecting member are screwed together, and the connecting member is rotated to adjust the front-to-back position of the contact arm, and the adjustment mechanism is provided. The adjustment mechanism has a female thread formed on one of the two members, the contact arm and the connecting member, a male thread formed on the other of the two members, and a radial gap formed between the female thread and the male thread. A driving tool in which the size of the radial gap is the difference between the thread diameter of the male thread and the root diameter of the female thread, and is 4 to 10% of the root diameter.

2. The driving tool according to claim 1, The male and female threads are a driving tool having the same size and pointed thread height.

3. A driving tool according to claim 1 or 2, The adjustment mechanism is a driving tool having the female thread formed on the contact arm and the male thread formed on the connecting member.

4. A driving tool according to any one of claims 1 to 3, A driving tool in which the effective diameter of the male thread is smaller than the effective diameter of the female thread.

5. A driving tool according to any one of claims 1 to 4, The connecting member has a dial that is rotated by the user. A driving tool in which the outer surface of the dial around its axis is exposed to the outside within a range of 180 degrees or less.

6. A driving tool according to any one of claims 1 to 5, The connecting member has a shaft that extends forward and backward, A driving tool in which the male or female thread is formed on the front part of the shaft, and the rear part is supported by a main support part of the tool body so as to be able to move back and forth.

7. The driving tool according to claim 6, The main body support portion has a hole through which the rear portion of the shaft is inserted, and the central axis of the hole is located closer to the tool body than the central axis of the shaft.

8. The driving tool according to claim 5, A driving tool having a contact portion that comes into contact with the rear of the arm when the dial is pushed from the side exposed to the outside toward the tool body.

9. The driving tool according to claim 5, A driving tool having a structure such that when the dial is pushed from the side exposed to the outside toward the tool body, the rear part of the arm does not come into contact with the tool body.

10. The driving tool according to claim 3, A driving tool in which the rear portion of the arm is formed of a plate-shaped metal, and the female screw is formed as part of the plate-shaped metal.

Images