DRIVE TOOL

Abstract

A driving tool (10) has a contact arm (6) and a connecting element (7). The position of the contact arm (6) can be adjusted in a forward-reverse direction by rotating the connecting element (7) via an adjustment mechanism (8). The adjustment mechanism (8) has an external thread (8a) and an internal thread (8b) with a radial clearance (8c) between them. The magnitude of the radial clearance (8c), which is the distance between the crown diameter (D1) of the external thread (8a) and the core diameter (D2) of the internal thread (8b), is between 4% and 10% of the core diameter (D2).

Description

TECHNICAL AREA

[0001] The present invention relates generally to a driving tool for driving a drive-in component, such as a nail or a staple, into a workpiece, such as wood or other materials. BACKGROUND

[0002] Driving tools are known which are designed to drive (drive, hammer, push) fasteners, such as nails or staples, and eject them from an ejection opening. Generally, such a driving tool has a contact arm located at the front of the ejection opening, which is movable in a rearward direction. A rear portion of the contact arm is connected to a linkage that is movable in a forward-backward direction relative to the main body of the driving tool. When a driving operation is performed, the contact arm is pressed against the workpiece to move the contact arm in the rearward direction relative to the main body of the tool. A trigger on the main body of the tool is then pressed (pulled). When both the contact arm and the trigger are actuated, the fastener is driven in through the ejection opening of the driving tool.

[0003] JP 7 107 650 B2 discloses a driving tool with an adjustment mechanism for adjusting the position of the contact arm in the front-back direction relative to the ejection opening. The adjustment mechanism has an internal thread (female thread) formed on the contact arm and an external thread (male thread) formed on the shank of the connecting component. The connecting component has a rotary knob that can be turned by a user. Turning the rotary knob causes the shank to rotate along with the rotary knob, and the contact arm moves in the front-back direction relative to the shank. Because of this configuration, the position of the contact arm in the front-back direction is adjustable, and consequently, the driving depth of the driving component being driven into the workpiece is also adjustable.

[0004] In the configuration described above, as in Fig. As shown in Figure 9, for example, the user turns a rotary knob 101 while pushing it towards the main tool body 100. This causes the rotary knob 101 and the shaft 102 to tilt towards the main tool body 100. Consequently, the contact arm 103 is pushed through the shaft 102, and the contact arm 103 is tilted relative to the shaft 102. This causes the external thread 104 and the internal thread 105 to bind (tear out, damage each other), thereby increasing the actuation force on the rotary knob 101. This can impair the operability of the rotary knob 101. BRIEF SUMMARY

[0005] Therefore, there is a need for a driving tool that is less likely to impair the operability of a rotary knob and other components.

[0006] The above-mentioned problem is solved by a driving tool according to claim 1.

[0007] The present disclosure relates to a driving tool equipped with a contact arm projecting forward from an ejection opening. A rear portion of the contact arm is connected to a connecting component. An adjustment mechanism, which screws (secures) the rear portion of the contact arm to the connecting component, allows the position of the contact arm to be adjusted in the forward-backward direction by rotating the connecting component. The adjustment mechanism has an external thread and an internal thread, with radial play between them. The external thread is formed on either the contact arm and the connecting component, while the internal thread is formed on the other.Radial play is defined as the difference between the crown diameter (major diameter) of the external thread and the minor diameter (minor diameter) of the internal thread, and its magnitude is specified to be 4% to 10% of the minor diameter. The crown diameter is the length of the diameter connecting the crowns of the external threads in the radial direction. The minor diameter is the length of the diameter connecting the bottoms of the troughs of the internal threads in the radial direction. Radial play allows for a slight "ratcheting" of the adjustment mechanism, thereby reducing the likelihood of jamming (pulling out, damage) and deterioration of the operability of the connected component, even if the threads are misaligned or inclined. BRIEF DESCRIPTION OF THE DRAWINGS Fig. Figure 1 is a left side view of a driving tool according to a first embodiment of the present disclosure without a left housing. Fig. 2 is a cross-sectional view along a line II-II in Fig. 1. Fig. Figure 3 is a perspective view of an adjustment mechanism seen from the front. Fig. Figure 4 is a perspective view of the adjustment mechanism seen from the rear. Fig. Figure 5 is a cross-sectional view along line VV in Fig. 1. Fig. Figure 6 is an enlarged schematic view of the external thread and the internal thread. Fig. Figure 7 is a perspective view from the rear of an adjustment mechanism according to a second embodiment of the present disclosure. Fig. Figure 8 is a cross-sectional view of a connection area, seen from above. Fig. Figure 9 is a cross-sectional view corresponding to Fig. 5 and represents the conventional adjustment mechanism. DETAILED DESCRIPTION

[0008] The detailed description that follows, with reference to the attached drawings, is intended to be a description of exemplary embodiments of the present disclosure and is not intended to be limiting and / or to represent only the embodiments in which the present disclosure can be carried out. The term "exemplary," used throughout this description, means "serving as an example, application, or illustration" and should not necessarily be considered preferred or advantageous over other exemplary embodiments. The detailed description includes specific details for the purpose of providing a consistent understanding of the exemplary embodiments of the disclosure.It is evident to the person skilled in the art that the exemplary embodiments of the disclosure can be carried out without these specific details. In some applications, the specific details relate to known structures, components and / or devices shown in block diagram form to avoid obscuring significant aspects of the exemplary embodiments presented herein.

[0009] According to the further aspect of the disclosure, the external thread and the internal thread have the same basic triangular height. Therefore, even if there is radial play, the external thread engages easily with the internal thread.

[0010] According to another aspect of the present disclosure, the adjustment mechanism has an internal thread formed on the contact arm and an external thread formed on the connecting component. Therefore, the external thread is formed on the rotatable connecting component. Accordingly, the external thread can be easily installed on the rotating shaft of the connecting component.

[0011] According to another aspect of the present disclosure, the flank diameter of the external thread is smaller than that of the internal thread. Therefore, the radial clearance between the external thread and the internal thread can be easily achieved.

[0012] According to another aspect of the present disclosure, the connecting component has a rotary knob that can be rotated by a user. The outer circumferential surface of the rotary knob about its axis is exposed to the outside within 180 degrees or less. Therefore, the user pushes and rotates the rotary knob from one direction. Even in such a case, the radial play prevents twisting (tilting, warping) between the external thread and the internal thread.

[0013] According to another aspect of the present disclosure, the connecting component has a shaft extending in the front-back direction. The external or internal thread is formed in the front portion of the shaft. The rear portion of the shaft is movably mounted in the front-back direction by a main body bearing area of ​​a tool body. The adjustment mechanism screws the rear portion of the contact arm to the front portion of the shaft. Due to this configuration, the contact arm and the shaft can be arranged side by side in the front-back direction.

[0014] According to another aspect of the present disclosure, the main body bearing area has a hole through which the rear portion of the shank is inserted. The central axis of the hole is configured such that it is positioned closer to the main tool body than the central axis of the shank. Therefore, when the user pushes the connecting component toward the main tool body, the central axis of the hole and the central axis of the shank are brought closer together. Consequently, the connecting component can be rotated easily and smoothly.

[0015] According to another aspect of the present disclosure, the driving tool has a contact area that touches the rear portion of the contact arm when the rotary wheel is pressed towards the main tool body from the side on which the rotary wheel is exposed. Therefore, the contact area supports the rear portion of the contact arm when the connecting component is actuated. Because of this configuration, the contact area can reduce looseness (rattling) of the adjustment mechanism.

[0016] According to another aspect of the present disclosure, when the rotary knob is pressed towards the main tool body from the side on which the rotary knob is exposed to the outside, the rear portion of the contact arm does not come into contact with the main tool body. Also, in a case where the configuration of the adjustment mechanism tends to rattle, the radial play reduces the twisting (twisting, tilting) between the external thread and the internal thread.

[0017] According to another aspect of the present disclosure, the rear region of the contact arm is formed from a metal sheet, and the internal thread is formed as part of the metal sheet. This makes it advantageous to form the internal thread as a single component with the rear region of the contact arm.

[0018] A first embodiment of the present disclosure is described below with reference to Fig. 1 to 6 described. As in Fig. As shown in Figure 1, a driving tool 10 is a gas spring-type driving tool that uses, for example, gas pressure to drive in a component. In the following description, a driving direction of the component (nail or staple) is defined as a forward direction, and a direction opposite to the driving direction is defined as a backward direction. The user grips the driving tool 10 with their hand and is positioned behind the driving tool 10 (at the rear). Fig. 1) An up-down direction and a left-right direction are defined based on the user's position.

[0019] As in Fig. As shown in Figure 1, the driving tool 10 has a main tool body 1 with a tubular housing 1a. As shown in Fig. As shown in Figure 2, the housing 1a encloses a cylindrical cylinder 1b that extends in a front-back direction. Inside the cylinder 1b is a piston 1c that can move backward and forward. The rear portion of the cylinder 1b, located behind the piston 1c, is connected to a storage chamber 1d. The storage chamber 1d is filled with compressed gas, such as air, and the pressure of the gas provides a thrust force that drives the piston 1c forward.

[0020] As in Fig. As shown in Figure 1, a drive lug 1e is located on the front of the housing 1a. The drive lug 1e contains a drive passage 1f, the rear end of which connects to the front area of ​​the cylinder 1b. A magazine 2 is attached to the underside of the drive lug 1e. The magazine holds several drive components vertically. The drive components are fed one after the other from the magazine 2 upwards into the drive passage 1f.

[0021] As in Fig. As shown in Figure 1, the drive lug 1e is provided with a contact arm 6 that is slidably movable in the front-back direction. The contact arm 6 is pre-tensioned such that it moves forward relative to the drive lug 1e (off position). When it is pressed against the workpiece, the contact arm 6 moves backward relative to the drive lug 1e (on position).

[0022] As in Fig. As shown in Figure 1, a handle 11 for the user is located on the lower part of the main tool body 1. A push button 12, which the user presses (pulls) with their finger, is located on the upper front surface of the handle 11. A push-button switch 13 inside the handle 11 is switched between an on-off state when the push button 12 is pressed. However, pressing the push button 12 is only effective when the contact arm 6 is pressed against a workpiece and is in the "on" position.

[0023] As in Fig. As shown in Figure 1, a battery mounting area 14 is arranged on a lower surface of the handle 11, extending in the front-back direction. The battery pack 15 can be removably attached to the battery mounting area 14. The battery pack 15 can be attached to and removed from the battery mounting area 14 by sliding it in the front-back direction. When removed from the battery mounting area 14, the battery pack 15 can be recharged for repeated use by an associated charger. The battery pack 15 can be used as a power source for other power tools. The battery pack 15 acts as a power source to supply power to an electric motor 3, etc.

[0024] As in Fig. As shown in Figure 1, a drive section housing 16, which is formed in an approximate tubular shape, is arranged at the front of the handle and extends in the top-bottom direction. An upper region of the drive section housing 16 is integrally connected to the housing 1a. A connecting section 17 is formed between the drive section housing 16 and the battery mounting area 14. The handle 11, the connecting section 17, the drive section housing 16, and the housing 1a cooperate to form a loop shape. The connecting section 17 accommodates a control unit 18. The control unit 18 primarily controls the driving of the electric motor 3.

[0025] As in Fig. As shown in Figure 1, a motor 3, serving as a drive source, is housed inside the drive section housing 16. The electric motor 3 is mounted such that its motor shaft 3a extends in the top-bottom direction. The electric motor 3 is powered by the battery pack 15 and activated by pressing the push button 12. A reduction gear 3b is located above the electric motor 3. A lifting mechanism 4 is also located above the reduction gear 3b. The electric motor 3, the reduction gear 3b, and the lifting mechanism 4 are arranged coaxially with the motor shaft 3a. A rotary output from the electric motor 3 is reduced by the reduction gear 3b and transmitted to the lifting mechanism 4 (see Figure 1). Fig. 2).

[0026] As in Fig. As shown in Figure 2, the lifting mechanism 4 is positioned on the right side of the drive lug 1e. The lifting mechanism 4 has a rotatable wheel 4a which rotates coaxially with the electric motor 3. The wheel 4a rotates in a direction indicated by an arrow R (counterclockwise). Fig. 2) The wheel 4a is configured such that it is restricted from rotating in a direction opposite to direction R. The wheel 2c has six engagement areas 4b, which are arranged along an outer circumferential edge of the wheel 4a. The engagement areas 4b are cylindrical shaft components (pins) that extend in the top-bottom direction.

[0027] As in Fig. As shown in Figure 2, an elongated drive 5, extending in the front-back direction, is coupled to a front surface of the piston 1c. A pointed end of the drive 5 enters the drive passage 1f. The drive 5 has six engaged areas 5a. Each of the engaged areas 5a projects to the right from a right side of the drive 5. Each engaged area 5a is formed in the shape of a rack tooth. The engaged areas 5a are arranged at regular intervals along the longitudinal direction of the drive 5 (in the front-back direction). Each of the engaged areas 5a engages sequentially with a corresponding engaged area 4d of the lifting mechanism 4.

[0028] In Fig. 2. The drive unit 5 is in its ready position and prepared for a drive operation. An engagement area 4b is engaged with a corresponding engaged area 5a. Specifically, the front-end rack tooth 5b, which is the foremost engaged area of ​​the engaged areas 5a, engages with the pin 4c at the rear end, which is located at the rear end in the direction of rotation of the wheel 4a. The last engagement pin 4c engages the front-end rack tooth 5b from the front. Due to the engagement of the last engagement pin 4c with the front-end rack tooth 5b and the rotation restriction of the wheel 4a in the direction opposite to direction R, the lifting mechanism 4 supports the drive unit 5 from the front. Accordingly, the drive unit 5 and the piston 1c are held in the ready position against the gas pressure in the storage chamber 1d.

[0029] Referring to Fig. 1. When the driving tool 10 is used, the user grasps the handle 11. The user then pushes the contact arm 6 against the workpiece from behind. This causes the contact arm 6 to move backward relative to the driving nose 1e. When the user presses the trigger 12 while the contact arm 6 is moving backward relative to the driving nose 1e, the control unit 18 operates the electric motor 3 so that it rotates. The rotation of the electric motor 3 is thereby transmitted to the lifting mechanism 4 via the reduction gear 3b.

[0030] As in Fig. As shown in Figure 2, the wheel 4a rotates in the direction indicated by arrow R. Due to the rotation of the wheel 4a, the last engagement pin 4c pushes the front-end rack tooth 5b from the front in a rearward direction. This movement unlocks the front-end rack tooth 5b from the last engagement pin 4c. Consequently, the piston 1c moves due to the gas pressure in the storage chamber 1d. The tip end of the drive 5 then drives in a drive component loaded into the drive passage 1f.

[0031] The drive-in component, driven by the drive 5, is ejected from the ejection opening 1j, located at the front end of the drive nose 1e. The ejected drive-in component is driven into the workpiece. When the piston 1c reaches the bottom of its travel, it collides with a damper 1r to stop the forward movement of the piston 1c and the drive 5. The damper 1r absorbs the impact of the piston 1c upon contact, thus preventing damage to the piston 1c.

[0032] After the piston 1c stops its forward movement, the wheel 4a continues to rotate in the direction R of rotation of the wheel 4a. Due to this movement, the engagement area 4b at the front end, in the direction R of rotation of the wheel 4a, engages with the rearmost engaged area 5a from the front. As the wheel 4a continues to rotate, the engagement areas 4b sequentially push the corresponding engaged areas 5a backward. In this way, the lifting mechanism 4 moves the drive pin 5 and the piston 1c back to the ready position.

[0033] As in Fig. As shown in Figure 1, the contact arm 6 is an elongated metal component extending in the front-back direction. The front portion of the contact arm 6a is located close to the ejection opening 1j. The middle portion of the contact arm 6b extends within the drive lug 1e in the front-back direction. Referring to Fig. 4, the rear area of ​​the contact arm 6c extends from the middle area of ​​the contact arm 6b in the direction to the left and bends downwards along the left side of the drive lug le.

[0034] As in Fig. 3 and Fig. As shown in Figure 4, the rear portion of the contact arm 6c is formed in a thin plate shape. A thin, disc-shaped connecting portion 6d extends downwards from the lower rear portion of the contact arm 6c, bent further to the left. A shaft 7a of a connecting component 7 is connected to the disc-shaped connecting portion 6d. The shaft 7a passes through the connecting portion 6d in the front-back direction. The shaft 7a is a cylindrical component that extends along the main tool body 1 in the front-back direction. The rear portion of the shaft 7a is inserted into a hole 1m, which is located in a main body bearing area 1k of the main tool body 1. The shaft 7a is supported by the main body bearing area 1k in such a way that it is rotatable and movable in the front-back direction relative to the main body bearing area 1k.

[0035] As in Fig. 5 and Fig. As shown in Figure 6, the connection area 6d has an internal thread (female screw) 8b, while the front part of the shaft 7a has an external thread (male screw) 8a. The shaft 7a is connected to the connection area 6d by being screwed onto the internal thread 8b. Rotating the shaft 7a about its axis causes the contact arm 6 to move in the front-back direction relative to the shaft 7a, and this movement adjusts the position of the contact arm 6 relative to the ejection opening 1j in the front-back direction. The position of the contact arm 6 relative to the ejection opening 1j in the front-back direction, in turn, controls the insertion depth of the insertion component into a workpiece. The external thread 8a and the internal thread 8b mentioned above form the adjustment mechanism 8. Each of the external thread 8a and the internal thread 8b mentioned above is a metric coarse thread with a nominal diameter of, for example,M6 is formed in the present embodiment.

[0036] As in Fig. As shown in Figure 3, a rotary wheel 7b is integrally attached to the outer circumference of the shaft 7a. The outer circumferential surface of the rotary wheel 7b has a concave-convex shape. The rotary wheel 7b is arranged coaxially with the shaft 7a. The rotary wheel 7b rotates together with the shaft 7a. The outer circumference of the rotary wheel 7b is exposed through a window 1n in the housing 1a in the outer direction (exposed area 7c) (see lower side in Figure 3). Fig. 3) The exposed area 7c of the rotating wheel 7b is exposed over a portion smaller than half of its total circumference. Specifically, the exposed area 7c is exposed over a portion of approximately 160 degrees.

[0037] When the user turns the rotary knob 7b, the exposed area 7c is pressed towards the main tool body 1. As the rotary knob 7b turns, the shaft 7a rotates. This allows the position of the contact arm 6 relative to the shaft 7a to be adjusted in the front-back direction, as described above. Fig. As shown in Figure 5, the shaft 7a is moved to the right by the force of the user pressing the rotary knob 7b. Specifically, a front section of the shaft 7a is moved to the right, closer to the main tool body 1, using the connection with the main body bearing area 1k as a pivot point.

[0038] Accordingly, when the user turns the rotary knob 7b, the external thread 8a tilts relative to the internal thread 8b, as if drawn by an imaginary line in Fig. Figure 6 shows that in the present embodiment, a radial clearance 8c is formed between the external thread 8a and the internal thread 8b along the entire length of the shaft 7a. This radial clearance 8c can absorb the inclination of the external thread 8a. In other words, even if the external thread 8a is inclined, it is less likely to significantly interfere with the internal thread 8b. Therefore, it is less likely that the external thread (screw) 8a and the internal thread (screw) 8b will twist (become twisted or jammed), thus allowing the external thread 8a to rotate smoothly without binding (seizing) on ​​the internal thread 8b. Accordingly, the user can turn the rotary knob 7b with ease and good control.

[0039] With reference to Fig. In this embodiment, the radial clearance 8c is formed by making the crown diameter (major diameter) D1 of the external thread 8a smaller than the nominal diameter M6 of the external thread 8a. More specifically, the crown diameter D1 is defined within a range of 90% to 96% of the nominal diameter M6 (i.e., 6 mm diameter). More preferably, the crown diameter D1 is defined within a range of 94% to 96% of the nominal diameter M6. In this embodiment, for example, D1 is defined to be approximately 5.7 mm, which corresponds to approximately 95% of the nominal diameter M6.

[0040] Regarding the internal thread 8b, the minor diameter (secondary diameter) D2 of the internal thread 8b is equal to the nominal diameter M6 of the internal thread 8b. The radial clearance 8c is defined as the difference between the minor diameter D2 and the crown diameter D1. Therefore, the radial clearance 8c is designed to be within a range of 4% to 10%, preferably 4% to 6%, of the minor diameter D2 of the internal thread 8b. The magnitude of the radial clearance 8c is set such that it is less than the basic triangular height H1 of the external thread. Due to this configuration, even with the radial clearance 8c, the external thread 8a and the internal thread 8b are not completely disengaged from each other, and the external thread 8a and the internal thread 8b can be properly screwed together.

[0041] As described above, reducing the crown diameter D1 of the external thread 8a results in a pitch diameter (effective diameter) R1 of the external thread 8a that is smaller than the pitch diameter R2 of the internal thread 8b. The dimensions, angles, and pitches of the threads of the external thread 8a are the same as those of a metric coarse thread with a nominal diameter of M6. Therefore, the basic triangular height H1 of the external thread 8a and the basic triangular height H2 of the internal thread 8b are the same size.

[0042] In the present embodiment, the engagement length (engagement span) of the thread of the external thread 8a with respect to the internal thread 8b lies in a range of 3.5% to 5.6% for a nominal diameter M6. A standard engagement length of an external thread is specified to be approximately 7% for a nominal diameter M6, and thus the engagement length (in the range of 3.5% to 5.6%) of the external thread 8a is specified to be 50% to 80% of that of the standard M6 screw. More preferably, the engagement length is specified to be in a range of 70% to 80% of that of the standard M6 screw. In the present embodiment, the engagement length of the external thread 8a is specified to be approximately 0.31 mm. This value is approximately 5.2% of the nominal diameter M6 and approximately 74% of the engagement length of the standard M6 screw.

[0043] The rear section 6c of the contact arm 6 and the connection section 6d are formed by bending a metal sheet. The internal thread 8b is formed as a single component comprising the rear section 6c and the connection section 6d. Therefore, the internal thread 8b is generally designed to accommodate large deviations in both positional and angular accuracy relative to the screw 8a. For this reason, the external thread 8a can be screwed in at an angle relative to the internal thread 8b, even in its natural state. However, even in such a configuration, interference between the external thread 8a and the internal thread 8b is less likely because the flank diameter R1 of the external thread 8a is smaller than the flank diameter R2 of the internal thread 8b.As a result, it is less likely that the external thread 8a and the internal thread 8b will twist (tilt, warp) (twisting between the external thread 8a and the internal thread 8b can be effectively reduced).

[0044] As in Fig. As shown in Figure 4, a bracket 9 is arranged behind the rotary wheel 7b. The bracket 9 has a rotary wheel bearing area 9a that supports the rear surface of the rotary wheel 7b over its entire circumference. A compression spring 1p is arranged between the rotary wheel bearing area 9a and the main body bearing area 1k. The compression spring 1p biases the rotary wheel bearing area 9a of the bracket 9 forward. Therefore, the shaft 7a is biased forward along with the rotary wheel 7b. Accordingly, the contact arm 6 is biased forward relative to the drive lug 1e.

[0045] As in Fig. 4 and Fig. As shown in Figure 5, the bracket 9 has an arm bearing area 9b that projects to the right of the rotary wheel bearing area 9a and then bends forward. The arm bearing area 9b supports the rear section 6c of the contact arm 6 from the right side. The arm bearing area 9b is supported from the right by the contact area 2a formed at the magazine 2. Because of this configuration, the rear section 6c of the contact arm 6 is supported from the right by the contact area 2a of the magazine 2 via the arm bearing area 9b. Therefore, when the user presses the exposed section 7c of the rotary wheel 7b, it is relatively difficult to move the rear section 6c of the contact arm 6 to the right (towards the main tool body 1). This makes it easier to prevent rotation between the external thread 8a and the internal thread 8b.

[0046] As in Fig. 3 and Fig. As shown in Figure 6, the insertion tool 10 has a contact arm 6 that projects forward from the ejection opening 1j. The rear section 6c of the contact arm 6 is attached to the connecting component 7 via the adjustment mechanism 8 for screwing (securing) the rear section 6c to the connecting component 7. The adjustment mechanism 8 allows the user to rotate the connecting component 7 in the forward-backward direction to change the position of the contact arm 6. The adjustment mechanism 8 has an external thread 8a, an internal thread 8b, and a radial clearance 8c formed between the external thread 8a and the internal thread 8b. The external thread 8a is located on either the contact arm 6 or the connecting component 7, whereas the internal thread 8b is located on the other of the two components. The radial clearance 8c is defined as a difference between the crown diameter D1 of the external thread 8a and the core diameter D2 of the internal thread 8b.Its size is between 4% and 10% of the core diameter D2. The apex diameter D1 is the length of the diameter connecting the apex of the external thread (male screw) 8a in the radial direction. The core diameter D2 is the length of the diameter connecting the bottoms of the troughs of the internal thread (female screw) 8b in the radial direction. Therefore, the radial play 8c allows the adjustment mechanism 8 to rattle slightly. This configuration prevents the threads, i.e., the external thread (male screw) 8a and the internal thread (female screw), from twisting or jamming, even if the external thread 8a and the internal thread 8b are misaligned or tilted, for example, due to the tilting of the connecting component 7. This reduces the risk of the connecting component 7 becoming difficult to turn and ensures that the adjustment mechanism 8 remains easy to operate.

[0047] As in Fig. As shown in Figure 6, the external thread 8a and the internal thread 8b have the same basic triangle heights H1 and H2. Therefore, even if radial clearance 8c is present, the external thread 8a engages easily with the internal thread 8b.

[0048] As in Fig. As shown in Figure 6, the adjustment mechanism 8 has an internal thread 8b formed on the contact arm 6 and an external thread 8a formed on the connecting component 7. Therefore, the external thread 8a is formed on the rotatable connecting component 7. Accordingly, the external thread 8a can be easily installed on the rotating shaft of the connecting component 7.

[0049] As in Fig. As shown in Figure 6, the flank diameter R1 of the male screw 8a is smaller than the flank diameter R2 of the internal thread 8b. Therefore, the radial clearance 8c between the external thread 8a and the internal thread 8b can be easily achieved.

[0050] As in Fig. As shown in Figure 3, the connecting component 7 has a rotary knob 7b that can be rotated by the user. The outer circumferential surface of the rotary knob 7b about its axis is exposed to the outside within 180 degrees or less. Therefore, the user pushes and rotates the rotary knob 7b from one direction. Even in such a case, the radial clearance 8c prevents twisting (tilting) between the external thread 8a and the internal thread 8b.

[0051] As in Fig. 3 and Fig. As shown in Figure 4, the connecting component 7 has a shaft 7a extending in the front-back direction. The external thread 8a or the internal thread 8b is formed in the front region of the shaft 7a. The rear region of the shaft 7a is movably mounted in the front-back direction by the main body bearing area 1k of the tool body 1. The adjustment mechanism 8 screws the rear region 6c of the contact arm 6 to the front region of the shaft 7a. Due to this configuration, the contact arm 6 and the shaft 7a can be arranged side by side in the front-back direction.

[0052] As in Fig. As shown in Figure 5, the driving tool 10 has a contact area 2a that contacts the rear area 6c of the contact arm 6 when the rotary wheel 7b is pressed towards the main tool body 1 from the side on which the rotary wheel 7b is exposed. Therefore, the contact area 2a supports the rear area 6c of the contact arm 6 when the connecting component 7 is actuated. Because of this configuration, the contact area 2a can reduce any looseness (rattling) of the adjusting mechanism 8.

[0053] As in Fig. As shown in Figure 3, the rear region 6c of the contact arm 6 is made from a metal sheet, and the internal thread 8b is formed as part of the metal sheet. This allows the internal thread 8b to be formed cost-effectively as a single component with the rear region of the contact arm 6c.

[0054] The second embodiment of the present disclosure is described below with reference to Fig. 7 and Fig. 8 described. A driving tool 20 of the second embodiment has a main body bearing area 21 instead of the main body bearing area 1k in Fig. 4. Descriptions of the components and configurations common to the first embodiment are omitted using the same reference numerals, and only the components that differ from the first embodiment are described in detail.

[0055] Fig. 7 and Fig. Figure 8 represents a positional relationship between the posterior part of the shaft 7a and the main body support area 21. As in Fig. As shown in Figure 7, the main body support area 21 has a hole 22 through which the rear part of the shaft 7a passes. The shaft 7a is intentionally mounted such that it is offset in a lower left direction (downward to the left) relative to the center of the hole 22. Fig. Figure 8 shows a cross-sectional view of the shaft 7a and the main body bearing area 21 from above. In its natural state, the central axis 23 of the hole 22 is positioned to the right (in the direction of the main tool body 1).

[0056] The shaft 7a is mounted such that it is pressed against a left inner surface of the hole 22. When the user pushes the rotary knob 7b towards the main 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 user to rotate the shaft 7a relative to the main body bearing area 21 when pushing and turning the rotary knob 7b. Accordingly, the operability of the rotary knob 7b can be improved.

[0057] In Fig. 7 The rear section 26 of the contact arm 6 extends forward from the connection section 27 along the left side of the drive lug 1e in a "floating" state. The rear section 26 of the contact arm 6 is supported by the drive lug 1e at its forward-extending end. Due to this configuration, the connection section 27 is positioned relatively far from where the drive lug 1e provides support. Furthermore, as shown in Fig. As shown in Figure 8, the holder 24 lacks an arm bearing area 9b that projects from the rotary wheel bearing area 25. Therefore, the driving tool 20 does not have a right-side bearing for the connecting area 27. Consequently, the connecting area 27 does not contact the main tool body 1, even when the user pushes the rotary wheel 7b upwards and to the right.

[0058] Accordingly, when the user presses the rotary knob 7b, the connection area 27 tends to shift towards the main tool body 1. Even in such a configuration, the radial clearance 8c between the external thread 8a and the internal thread 8b can adequately absorb the mutual misalignment of the external thread and the internal threads 8a and 8b (see Fig. 6) Accordingly, it is less likely that the external thread 8a and the internal thread 8b will twist (tilt), and the rotary knob 7b can be turned easily and smoothly.

[0059] As above in relation to Fig. 7 and Fig. As described in Figure 8, the main body bearing area 21 has the hole 22 through which the rear portion of the shank 7a is inserted. The central axis 23 of the hole 22 is configured such that it is closer to the main tool body 1 than the central axis 7d of the shank 7a. Therefore, when the user pushes the connecting element 7 towards the main tool body 1, the central axis 23 of the hole 22 and the central axis 7d of the shank 7a are brought closer together. Consequently, the connecting element 7 can be rotated easily and smoothly.

[0060] As in Fig.As shown in Figure 8, when the rotary wheel 7b is pressed towards the main tool body 1 from the side on which the rotary wheel 7b is exposed to the outside, the rear area 26 of the contact arm 6 does not touch the main tool body 1. Even in a case where the configuration of the adjustment mechanism 8 tends to rattle, the radial play 8c reduces the twisting (tilting) between the external thread 8a and the internal thread 8b.

[0061] Various modifications can be made to each of the embodiments described above. In the embodiments described above, the driving tool is a gas spring-type driving tool. Alternatively, the present disclosure can be applied to a driving tool described as being of a mechanical type, in which, for example, the driving tool is moved in the opposite direction to the driving direction by a lifting mechanism to increase the spring force, such as that of a compression spring or the like, to move the driving tool in the driving direction. Furthermore, the present disclosure can be applied to a flywheel-type driving tool, a pneumatic-type driving tool with a compressor connection, etc., regardless of the driving method.

[0062] In the present disclosure, the crown diameter of the external thread is configured such that it is smaller in the radial direction than the nominal diameter of the external thread, resulting in a flank diameter of the external thread that is smaller than the flank diameter of the internal thread. Alternatively, the flank diameter of the internal thread can be configured to be smaller than the flank diameter of the external thread by making the root diameter of the internal thread larger in the radial direction than the nominal diameter of the internal thread. Furthermore, the external thread can be configured at the contact arm, and the internal thread can be configured at the connecting component. Additionally, the basic triangular height of the external thread can differ from the basic triangular height of the internal thread.The external and internal threads are not limited to a nominal diameter of M6 and can have any thickness as long as the nominal diameter is M12 or smaller.

[0063] The rear section of the contact arm and the connecting component can be located on the left side, the right side, the top side, or any other location on the main tool body. The contact area that supports the rear section of the contact arm can be located within the main tool body instead of the magazine.

[0064] It is explicitly emphasized that all features disclosed in the description and / or the claims are to be considered separate and independent of one another for the purposes of the original disclosure as well as for the purpose of limiting the claimed invention, irrespective of the combinations of features in the embodiments and / or the claims. It is explicitly stated that all range specifications or specifications of groups of units disclose every possible intermediate value or subgroup of units for the purposes of the original disclosure as well as for the purpose of limiting the claimed invention, in particular also as a boundary of a range specification. QUOTES INCLUDED IN THE DESCRIPTION

[0000] This list of documents cited by the applicant was automatically generated and is included solely for the reader's convenience. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions. Cited patent literature

[0000] JP 7 107 650 B2

[0003]

Claims

[1] Driving tool (10; 20), with a tool body (1), a contact arm (6) which projects forward from an ejection opening (1j), a connecting component (7) which is connected to a rear area (6c) of the contact arm (6), and an adjustment mechanism (8) configured to adjust the position of the contact arm (6) in a front-back direction by screwing a rear section (6c) of the contact arm (6) to the connecting component (7), wherein the adjustment mechanism (8) has an external thread (8a), an internal thread (8b) and a radial clearance (8c) between the external thread (8a) and the internal thread (8b), wherein the external thread (8a) is formed either on the contact arm (6) or the connecting part (7), while the internal thread (8b) is formed on the other side of the contact arm (6) and the connecting part (7), and the radial clearance (8c) is a difference between a crown diameter (D1) of the external thread (8a) and a core diameter (D2) of the internal thread (8b), and the magnitude of the radial clearance is between 4% and 10% of the core diameter (D2) of the internal thread (8b). [2] Driving tool (10; 20) according to claim 1, wherein the external thread (8a) and the internal thread (8b) have the same basic triangle height (H1, H2). [3] Driving tool (10; 20) according to claim 1 or 2, wherein the internal thread (8b) is formed at the contact arm (6) and the external thread (8a) is formed at the connecting component (7). [4] Driving tool (10; 20) according to one of claims 1 to 3, wherein a flank diameter (R1) of the external thread (8a) is smaller than that (R2) of the internal thread (8b). [5] Driving tool (10; 20) according to one of claims 1 to 4, wherein the connecting component (7) has a rotary wheel (7b) which can be rotated by a user, and an outer circumferential surface of the rotary wheel (7b) is exposed to an outside within a range of 180 degrees or less. [6] Driving tool (10; 20) according to one of claims 1 to 5, wherein the connecting component (7) has a shaft (7a) that extends in the front-back direction, the external thread (8a) or the internal thread (8b) is formed on a front area of ​​the shaft (7a), and a rear area of ​​the shaft (7a) is movably supported in the front-back direction by a main body support area (1k; 21) of the tool main body (1). [7] Driving tool (20) according to claim 6, wherein the main body support area (21) has a hole (22) through which the rear part of the shaft (7a) is inserted, and a central axis (23) of the hole (22) is positioned closer to the main tool body (1) than a central axis (7d) of the shaft (7a). [8] Driving tool (10; 20) according to claim 5, further comprising a contact area (2a) which touches the rear area (6c) of the contact arm (6) when the rotary wheel (7b) is pressed towards the main tool body (1) from a side on which the rotary wheel (7b) is exposed. [9] Driving tool (20) according to claim 5, wherein the main tool body (1) is configured such that when the rotary wheel (7b) is pressed towards the main tool body (1) from a side on which the rotary wheel (7b) is exposed, the rear area (6c) of the contact arm (6) is prevented from touching the main tool body (1). [10] Driving tool (10; 20) according to claim 3, wherein the rear area (6c) of the contact arm (6) is made of a metal sheet and the internal thread (8b) is made as a part of the metal sheet.

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