Driving tool

Abstract

There is a need for a drive tool that can suppress contact between the rotor and stator in a motor and prevent core friction. [Solution] The driving tool 1 has a driving mechanism 20, a power transmission mechanism 40, and a mechanism housing. The driving mechanism 20 biases the driver forward. The power transmission mechanism 40 moves the driver backward by the output of the motor 30. The mechanism housing houses the power transmission mechanism 40. The driving tool 1 has a motor housing 12, a fastening part 12b, and a main body housing 11. The motor housing 12 houses the motor 30. The fastening part 12b fastens the motor housing 12 to the mechanism housing with screws. The main body housing 11 covers the mechanism housing and exposes the motor housing 12.

Description

Technical Field

[0001] The present disclosure relates to a driving tool for driving a driving member into a driven material.

Background Art

[0002] Patent Document 1 discloses a so-called gas spring type driving tool. The driving tool has a driver, a driving mechanism, a motor, and a lifter. The driver moves in the driving direction by the driving mechanism and moves in the counter-driving direction by the lifter. The driving mechanism has a cylinder extending in the driving direction and a piston that is movable within the cylinder and is integral with the driver. The lifter is driven by the output of the motor being transmitted through a reduction gear or the like. When the lifter is driven to move the driver and the piston in the counter-driving direction, the gas pressure in the accumulator chamber provided in the counter-driving direction of the piston increases. The driver moves in the driving direction using this gas pressure as a driving force. A driving tool is sequentially supplied from a magazine to a driving passage in front of the driver in the driving direction. The driving member is driven into the driven material by being struck by the driver moving in the driving direction.

[0003] A mechanism that is driven by the output of the motor such as a reduction gear and a lifter being transmitted, and a driving mechanism that accumulates driving energy by the rotation of the lifter are housed in an integrally connected mechanism housing. Also, a bearing that rotatably supports the motor shaft is press-fitted into the mechanism housing. Therefore, the motor shaft and the rotor integral with the motor shaft are in a state of being supported by the mechanism housing. On the other hand, the stator of the motor is fixed in a motor housing separate from the mechanism housing. In conventional products, the motor housing is connected to the mechanism housing by a fastening structure such as an inlay structure. The driving tool is provided with a main body housing that further covers the mechanism housing and the motor housing from the outside. The mechanism housing and the motor housing are positioned relative to each other by being housed in the main body housing. That is, the motor housing is positioned without being fixed to the mechanism housing by fastening or the like.

[0004] The piston of the driving mechanism slides within the cylinder during the driving operation and collides with a cushion at the bottom dead center. The driver collides with the driving tool during the driving operation and then receives a reaction force from the material being driven via the driving tool. Vibrations caused by these sliding, collisions, and reaction forces are transmitted within the mechanism housing. These vibrations are also transmitted to the motor shaft and rotor, which are supported by the mechanism housing. On the other hand, the stator and motor housing are not fixed to the mechanism housing and therefore do not follow the vibrations that occur in the mechanism housing. As a result, when vibrations occur on the mechanism housing side, the rotor and stator may come into contact, potentially causing core friction. Thus, there was room for improvement in the driving tool to suppress motor core friction. [Prior art documents] [Patent Documents]

[0005] [Patent Document 1] Japanese Patent Publication No. 2024-103124 [Overview of the project] [Problems that the invention aims to solve]

[0006] Therefore, there is a need for a drive tool that can suppress contact between the rotor and stator in a motor and prevent core friction. [Means for solving the problem]

[0007] According to one feature of this disclosure, a driving tool has a driving mechanism, a power transmission mechanism, and a mechanism housing. The driving mechanism biases the driver forward. The power transmission mechanism moves the driver backward by the output of a motor. The mechanism housing houses the power transmission mechanism. The driving tool has a motor housing, a fastening part, and a main body housing. The motor housing houses a motor. The fastening part screws the motor housing to the mechanism housing. The main body housing covers the mechanism housing and exposes the motor housing.

[0008] Therefore, the mechanism housing that rotatably supports the motor shaft and rotor and the motor housing that supports the stator are fastened together with screws. As a result, the motor housing follows the vibrations generated in the power transmission mechanism within the mechanism housing. This makes it possible to make the vibrations transmitted from the mechanism housing to the rotor and the vibrations transmitted from the mechanism housing to the stator via the motor housing the same vibration mode. Therefore, contact between the rotor and stator due to vibration transmission can be suppressed. In this way, contact between the motor rotor and stator can be suppressed and core friction can be prevented.

[0009] Furthermore, by exposing the motor housing from the main housing, the size of the area surrounding the motor housing can be suppressed. This increases the flexibility of the placement of structures near the motor housing, such as the magazine and handle, allowing the entire driving tool to be made more compact. [Brief explanation of the drawing]

[0010] [Figure 1] This is a perspective view of the driving tool related to this disclosure, taken from the upper left front. [Figure 2] This is a left side view of the driving tool. [Figure 3] This is a left side view of the driving tool with the pusher lowered and held in place. [Figure 4] This is a front view of the driving tool. [Figure 5] This is a cross-sectional view taken along line VV in Figure 2. [Figure 6] This is a cross-sectional view taken along the line VI-VI in Figure 2. [Figure 7] This is a cross-sectional view taken along the line VII-VII in Figure 6 when the driver has moved to the bottom dead center. [Figure 8] This is a cross-sectional view taken along line VII-VII in Figure 6 when the driver is in the standby position. [Figure 9] This is a perspective view of the driving tool, seen from the lower left front. [Figure 10] This is a cross-sectional view taken along line XX in Figure 2. [Figure 11] It is a right side view of the driving tool. [Figure 12] It is a right side view of the driving tool in a state where the right housing of the main body housing having a split structure is removed. [Figure 13] It is an exploded perspective view disassembled into a mechanism part, a motor housing, and a main body housing. [Figure 14] It is a perspective view of the speed reduction mechanism. [Figure 15] It is an exploded perspective view of the stopper. [Figure 16] It is a sectional view taken along line XVI-XVI in FIG. 5 as viewed in the direction of the arrow when the inner ring of the stopper rotates forward. [Figure 17] It is a sectional view taken along line XVI-XVI in FIG. 5 as viewed in the direction of the arrow when the inner ring of the stopper rotates backward. [Figure 18] It is an exploded perspective view of the buffer mechanism as viewed from the upper left front. [Figure 19] It is an exploded perspective view of the buffer mechanism as viewed from the upper right front. [Figure 20] It is a sectional view taken along line XX-XX in FIG. 6 as viewed in the direction of the arrow.

Embodiments for Carrying Out the Invention

[0011] According to another feature of the present disclosure, the motor housing is cylindrical. The cylindrical fastened portion of the mechanism housing to which the fastening portion is screwed is exposed from the main body housing. Therefore, it is possible to further suppress the transmission of vibration from the mechanism housing to the motor housing via the main body housing. In addition, the compactness around the motor housing can be further enhanced. Further, by fastening the cylindrical motor housing to the cylindrical fastened portion, the airtightness and rigidity of the motor housing and the mechanism housing can be made the same as those of the conventional structure while being compact.

[0012] According to another feature of the present disclosure, the main body housing has an upper housing, a handle housing, and a lower housing. The upper housing houses the mechanism housing. The handle housing extends downward from the upper housing and bears the handle. The lower housing projects forward from the lower part of the handle housing and is connected to the lower part of the motor housing.

[0013] For example, consider the case where vibration is transmitted from the mechanism housing to the lower part of the motor housing via the main body housing. In this vibration transmission path, the upper housing, the handle housing, and the lower housing are interposed. And the main body housing is provided with a material having a lower rigidity than that of the motor housing or the like. If vibration is transmitted through this transmission path, mainly the handle housing deflects. Therefore, the vibration is reduced before being transmitted to the lower housing. Thereby, the transmission of vibration to the motor housing via the main body housing can be suppressed. Thus, it is possible to suppress the transmission of vibration to the motor housing from other than the mechanism housing. As a result, the vibration modes of the rotor and the stator can be made more consistent, and core rubbing can be suppressed.

[0014] According to another feature of the present disclosure, an elastic member is provided between the upper housing and the mechanism housing. Therefore, by absorbing vibration with the elastic member, the vibration transmitted from the mechanism housing to the upper housing can be efficiently reduced.

[0015] According to another feature of the present disclosure, the elastic member is a rubber ring held in an elastically deformed state between the outer surface of the mechanism housing and the inner surface of the upper housing. Therefore, the mechanism housing and the upper housing are connected with the rubber ring sandwiched therebetween in a wide range corresponding to the diameter of the rubber ring. Therefore, while suppressing the transmission of vibration from the mechanism housing to the main body housing, the stability of the main body housing holding the mechanism housing can be enhanced.

[0016] According to other features of this disclosure, the lower housing has a connecting portion. The connecting portion is connected to the lower part of the motor housing and positions the lower part of the motor housing. Therefore, the lower part of the motor housing and the connecting portion of the lower housing are connected and positioned relative to each other without the need for, for example, an elastic member. Thus, the motor housing is screw-fastened to the mechanism housing at the top and connected to the lower housing at the bottom, and is positioned in the vertical direction. This allows the motor housing to be held stably.

[0017] According to other features of this disclosure, a controller for controlling the motor is provided. The controller is housed in a lower housing. Therefore, by placing the controller near the motor, the wiring connecting the two can be made more compact. Moreover, the controller can be compactly positioned by utilizing the space below the motor.

[0018] According to other features of this disclosure, the driving tool has a fan, an air intake, and a ventilation passage. The fan rotates by the drive of a motor. The air intake is formed at the bottom of the lower housing. The ventilation passage introduces outside air, drawn in by the suction force of the fan from the air intake, into the motor housing from inside the lower housing. Therefore, the controller can also be cooled using the cooling air that cools the motor. Furthermore, by making the ventilation passage a simple path with fewer detours, the force of the cooling airflow can be maintained from the air intake to the exhaust.

[0019] According to other features of this disclosure, a magazine is provided that accommodates multiple driving tools and is long in the front-to-back and up-to-down directions. The controller is rectangular and is housed in the lower housing with a wide surface extending in the longitudinal direction aligned with the magazine. Outside air from the intake port flows between the inner surface of the lower housing and the wide surface in the left-to-right direction between the controller and the magazine. Therefore, the controller can be compactly positioned around the magazine. In addition, the controller can be efficiently cooled by directing cooling air onto the wide surface of the controller.

[0020] According to other features of this disclosure, a magazine for housing multiple driving tools is provided. The upper part of the magazine is connected to the mechanism housing. The lower part of the magazine is connected to the lower housing. Thus, the magazine is positioned vertically by being connected to the mechanism housing at the top and to the lower housing at the bottom. This allows the magazine to be held stably.

[0021] Next, a first embodiment of the present disclosure will be described with reference to Figures 1 to 20. As an example of a driving tool, a gas spring type driving tool 1 that utilizes the gas pressure of a pressure accumulator chamber as the thrust force for driving in the driving tool will be exemplified. The driving tool 1 exemplified is a tool called a fencing stapler that drives staples, which are driving tools N, into wooden posts or the like. With the driving tool 1, a fence made of metal wire together with the staples can be attached to posts or the like. In the following description, the direction in which the driving tool N is driven will be the forward direction, and the opposite direction will be the rear direction. The user of the driving tool 1 will generally be positioned behind the driving tool 1 and will grip the handle 4. The up, down, left, and right directions will be based on the direction as seen from the user.

[0022] <Overall structure of the driving tool 1> As shown in Figure 1, the driving tool 1 has a tool body 10 and a handle 4. The handle 4 extends downward from the tool body 10. The tool body 10 is equipped with a driving mechanism 20, a motor 30, and a power transmission mechanism 40. The driving mechanism 20 moves the driver 24 (see Figure 7) forward in the driving direction. The power transmission mechanism 40 transmits the output of the motor 30 to the driver 24. A lifter 60 (see Figure 7) is provided at the downstream end of the power transmission mechanism 40. The lifter 60 receives the output of the motor 30 and moves the driver 24 backward in the opposite direction of driving.

[0023] As shown in Figure 2, a trigger 5 is provided on the front upper part of the handle 4. An operating surface 5a is provided on the front of the trigger 5. A trigger switch 5b is provided behind the trigger 5 and inside the handle 4. The user can hook their finger onto the operating surface 5a while gripping the handle 4. The user pushes the operating surface 5a toward the handle 4 (rearward) with the finger hooked onto it. This causes the trigger switch 5b to be pressed by the trigger 5, changing from the off state to the on state. When the trigger switch 5b is in the on state, it transmits an on signal to the controller 35, which will be described later. When the driving nose portion 2 is pressed against the material to be driven W and moves backward, the operation of the trigger 5 becomes effective.

[0024] As shown in Figure 2, a main body housing 11 is provided to cover the driving mechanism 20 and the power transmission mechanism 40. The main body housing 11 is made of, for example, synthetic resin. The main body housing 11 includes an upper housing 11a, a handle housing 11b, and a lower housing 11d. The upper housing 11a covers the driving mechanism 20 and at least a part of the power transmission mechanism 40. The handle housing 11b is cylindrical and extends downward from the upper housing 11a, and constitutes the outer circumferential surface of the handle 4. A widening section 11c is connected to the lower part of the handle housing 11b. The widening section 11c is a rectangular box shape with a greater width in the front-rear and left-right directions than the handle housing 11b.

[0025] As shown in Figure 2, a battery mounting section 7 is provided on the lower surface of the widened section 11c. A battery 8 can be removably mounted in the battery mounting section 7. The battery 8 is mounted in the battery mounting section 7 by sliding it from rear to front. The battery 8 is removed from the battery mounting section 7 by sliding it from front to rear. When mounted in the battery mounting section 7, the battery 8 is located below the battery mounting section 7. The battery 8 supplies power to the motor 30, etc. The battery 8 can be removed from the battery mounting section 7 and repeatedly recharged with a separately prepared charger for reuse. The battery 8 can be used as a power source for other driving tools.

[0026] As shown in Figure 2, the lower housing 11d is connected to the front of the widened portion 11c of the handle housing 11b. The lower housing 11d is connected to the lower part of the motor housing 12, which houses the motor 30. The lower housing 11d houses a controller 35 that primarily controls the drive of the motor 30. The overall shape of the main body housing 11, to which the upper housing 11a, handle housing 11b, and lower housing 11d are connected, is C-shaped when viewed from the left and right sides. The motor housing 12 is positioned in the C-shaped opening of the main body housing 11 when viewed from the left and right sides.

[0027] As shown in Figure 4, the handle 4 and trigger 5 are positioned at approximately the same left-right position as the magazine 80, which will be described later. The left-right centers of the handle 4, trigger 5, and magazine 80 are roughly in the same position, for example, approximately the same position as the left-right center of the cylinder 21 (see Figure 6). The handle 4 and magazine 80 extend vertically, approximately parallel to each other. The motor housing 12 is located to the right of the trigger 5 and magazine 80, and is spaced apart from the trigger 5 and magazine 80 in the left-right direction. The motor housing 12 overlaps the handle 4 in the left-right direction at the top, but is spaced apart from the outer surface of the handle 4 in the left-right direction at the bottom. In a front-to-back view, there is a gap A between the motor housing 12 and the handle 4 in the left-right direction.

[0028] As shown in Figure 2, the motor housing 12 overlaps the magazine 80 in the left-right direction. The rear end of the motor housing 12 is located in front of the operating surface 5a of the trigger 5. As shown in Figure 10, the motor housing 12 is positioned to the right of the area between the magazine 80 and the trigger 5 in the front-rear direction.

[0029] As shown in Figure 2, the front of the tool body 10 is provided with a driving nose section 2. The driving nose section 2 has a driver guide 16 that extends in the front-rear direction. Inside the driver guide 16, there is a driving passage 2a that extends in the front-rear direction. At the front end of the driving passage 2a, an injection port 2b opens forward.

[0030] As shown in Figure 2, the driving nose portion 2 has a contact arm 3 that abuts against the material to be driven W. The contact arm 3 is slidable in the front-rear direction relative to the driver guide 16. The contact arm 3 is connected to an adjuster 6 by an adjuster connecting portion 3a. The adjuster 6 is provided on the left side of the driving nose portion 2. The adjuster 6 is rotatable about the axis of a rotating shaft 6a that extends in the front-rear direction. By rotating the adjuster 6, the front-rear position of the contact arm 3 relative to the driver guide 16 can be adjusted.

[0031] As shown in Figure 3, the adjuster 6 is biased forward relative to the driver guide 16 by a compression spring 6b. The contact arm 3, which is connected to the adjuster 6, is also biased forward relative to the driver guide 16 by a compression spring 6b. A switch 6c (see Figure 5) is provided behind the adjuster 6. As shown in Figure 2, pressing the contact arm 3 against the material to be driven W causes the contact arm 3 and the adjuster 6 to move backward. The switch 6c is turned from the off state to the on state by being pressed directly or indirectly via a spring or the like by the adjuster 6. When the switch 6c is on, it sends an on signal to the controller 35. When the on signal from the switch 6c is sent to the controller 35, the trigger 5 can be pulled. When the contact arm 3 is not pressed against the material to be driven W, the switch 6c is off and does not send an on signal. Therefore, the trigger 5 cannot be pulled.

[0032] <Driving mechanism 20> As shown in Figure 7, the driving mechanism 20 includes a cylinder 21, a piston 23, and a driver 24. The cylinder 21 is housed in the main body housing 11 in an orientation extending in the front-rear direction. The piston 23 is reciprocating back and forth within the cylinder 21. The driver 24 is connected to the front of the piston 23 in an orientation extending in the front-rear direction. Behind the piston 23, the rear end of the cylinder 21 communicates with a pressure accumulator 22. The pressure accumulator 22 is filled with compressed gas, such as air. The gas pressure in the pressure accumulator 22 acts as a thrust that biases the rear surface of the piston 23 forward.

[0033] As shown in Figure 7, the accumulator chamber 22 is connected to the air chamber 22a above the cylinder 21. The air chamber 22a extends forward from the rear end of the cylinder 21. The air chamber 22a extends to near the rear end of the lifter 60. The air chamber 22a extends forward to approximately the same position as the front end of the piston 23 at bottom dead center. The air chamber 22a is located behind the lifter 60. The upper end of the air chamber 22a and the upper end of the lifter 60 are at approximately the same height. As shown in Figure 13, the lower surface of the air chamber 22a is arc-shaped, covering the outer circumferential surface of the cylinder 21 from above. The upper surface of the air chamber 22a is arc-shaped, following the inner circumferential surface of the upper housing 11a.

[0034] As shown in Figure 7, a cylindrical cushion 25 is provided at the front of the cylinder 21. The cushion 25 is made of an elastic material such as rubber. The cushion 25 absorbs the forward impact of the piston 23 when it moves to the bottom dead center during the driving operation. A driver 24 is inserted through the center of the cushion 25. The front end 25a of the cushion 25 is located in front of the front end 21a of the cylinder 21. The front end 25a of the cushion 25 is located behind the rear end of the lifter housing 15 (described later) and at approximately the same fore-aft position as the rear end of the lifter 60. The front end 25a of the cushion 25 and the front end 21a of the cylinder 21 are located behind the operating surface 5a of the trigger 5. The front end of the piston 23 at bottom dead center is also located behind the operating surface 5a of the trigger 5.

[0035] As shown in Figure 7, the upper surface of the driver 24 is provided with a plurality of rack teeth 24a that protrude upward. In this embodiment, five rack teeth 24a are arranged in the front-to-back direction, which is the longitudinal direction of the driver 24. The rack teeth 24a are triangular in left and right side views. The front surface of the rack teeth 24a extends in a direction substantially perpendicular to the driving direction. The rear surface of the rack teeth 24a extends in a direction that is inclined forward toward upward. The rack teeth 24a are an example of an engaged part that engages with the engagement pin (engagement part) 63 of the lifter 60, which will be described later. The lifter 60 rotates with the bottom surface on the front side of the rack teeth 24a engaged with the engagement pin 63. As a result, the driver 24 and piston 23 move backward against the gas pressure of the accumulator chamber 22.

[0036] As shown in Figure 2, the driving tool N, which is housed in the magazine 80, is sequentially supplied one by one to the driving passage 2a by a pusher 81, which will be described later. The driving tool N is supplied to the driving passage 2a in a position where the head Na is located at the rear end, and the legs Nb extend forward from both the left and right ends of the head Na. As shown in Figure 7, the driver 24 moves forward due to the gas pressure in the pressure accumulator chamber 22 during the driving operation. The tip 24b located at the front end of the driver 24 strikes the head Na of one of the driving tools N supplied to the driving passage 2a forward. As a result, the driving tool N is ejected from the ejection port 2b and driven into the material W to be driven.

[0037] <Mechanism section 13> As shown in Figure 5, the tool body 10 is provided with a gear housing 14 and a lifter housing 15 as mechanism housings for the power transmission mechanism 40. The gear housing 14 houses the reduction mechanism 41 that reduces the output of the motor 30, which is part of the power transmission mechanism 40. The lifter housing 15 houses the lifter 60 of the power transmission mechanism 40. The gear housing 14 is covered by the main body housing 11 except for the lower fastened portion 14b. The lifter housing 15 is entirely covered by the main body housing 11.

[0038] As shown in Figure 13, the gear housing 14, lifter housing 15, cylinder 21, and pressure accumulator 22 are integrally connected by screw fastening. Although omitted in Figure 13 for clarity, the driver guide 16 is also screw-fastened to the lifter housing 15 and cylinder 21 (see Figure 12). In this disclosure, the structure including the gear housing 14, lifter housing 15, driver guide 16, cylinder 21, and pressure accumulator 22 is referred to as the mechanism 13. Each structure constituting the mechanism 13 is made of a material with higher rigidity than the main housing 11, such as aluminum or iron. Vibrations generated within the mechanism 13, such as vibrations associated with the sliding of the piston 23 or the movement of the driver 24, are transmitted within the mechanism 13 in the same vibration mode (see Figure 7). The mechanism 13 is generally covered by the upper housing 11a.

[0039] As shown in Figure 12, a cap 14a is screw-fastened to the right side of the gear housing 14. The cap 14a airtightly covers the gear housing 14. A cylindrical ring-holding portion 14c is recessed on the outer surface of the cap 14a. A rubber ring 18 is housed in the ring-holding portion 14c as an elastic member. The rubber ring 18 is elastically held between the ring-holding portion 14c on the outer surface of the cap 14a and the inner surface of the upper housing 11a (see Figure 5). As a result, the rubber ring 18 suppresses the transmission of vibrations from the gear housing 14 to the main housing 11.

[0040] As shown in Figure 13, a cap 15a is screw-fastened to the left side of the lifter housing 15. The cap 15a airtightly covers the lifter housing 15. A cylindrical ring-holding portion 15b is recessed on the outer surface of the cap 15a. A rubber ring 18 is housed in the ring-holding portion 15b as an elastic member. The rubber ring 18 is elastically held between the ring-holding portion 15b on the outer surface of the cap 15a and the inner surface of the upper housing 11a (see Figure 6). As a result, the rubber ring 18 suppresses the transmission of vibrations from the lifter housing 15 to the main housing 11.

[0041] <Motor 30 and motor housing 12 and surrounding structure> As shown in Figure 5, a motor shaft 30a is provided in the center of the motor 30. The motor shaft 30a extends vertically along the motor axis J1. The motor shaft 30a is rotatably supported at its lower part by a bearing 30d and at its upper part by a bearing 30e. The bearing 30d is inserted into a recess 12d formed in the lower part of the motor housing 12. The bearing 30e is press-fitted into a recess 14f formed in the lower part of the gear housing 14. A rotor 30b is integrally attached to the outer circumference of the motor shaft 30a. Therefore, the motor shaft 30a and rotor 30b are supported by the gear housing 14 (see Figure 13). As a result, vibrations from the mechanism 13 are transmitted to the motor shaft 30a and rotor 30b.

[0042] As shown in Figures 4 and 12, the motor housing 12 is cylindrical and extends in the vertical direction. The motor housing 12 is made of a material with higher rigidity than the main housing 11, for example, synthetic resin. A flange-shaped and rectangular cylindrical fastening portion 12b is provided at the top of the motor housing 12, extending radially outward from the cylindrical portion. As shown in Figure 5, the stator 30c is fixed to the inner circumferential surface of the motor housing 12. The stator 30c is located radially outward from the rotor 30b.

[0043] As shown in Figures 4 and 12, a flange-shaped, rectangular cylindrical fastening portion 14b is provided at the lower part of the gear housing 14. The fastening portion 14b has approximately the same outer circumference shape as the fastening portion 12b of the motor housing 12. The fastening portion 14b is exposed from the upper housing 11a. The fastening portion 12b of the motor housing 12 and the fastening portion 14b of the gear housing 14 are screw-fastened together by bolts 17. The bolts 17 are fastened from the lower fastening portion 12b towards the upper fastening portion 14b. The screw-fastening of the motor housing 12 and the gear housing 14 transmits vibrations of the same vibration mode as the mechanism 13 to the motor housing 12 and the stator 30c.

[0044] As shown in Figure 13, the lower outer circumference of the motor housing 12 is provided with a connecting portion 12c having a groove extending in the circumferential direction. The upper inner circumference of the lower housing 11d is provided with a connecting portion 11g having a rib extending in the circumferential direction. The connecting portion 11g can engage with the connecting portion 12c. The main housing 11 has a split structure divided into a right housing 11e and a left housing 11f in the left-right direction. The left and right split lower housings 11d sandwich the connecting portion 12c of the motor housing 12. As a result, the connecting portion 11g engages with the connecting portion 12c, and the motor housing 12 and the lower housing 11d are positioned relative to each other in the vertical direction.

[0045] As shown in Figure 5, a fan 31 is mounted on the upper part of the motor shaft 30a. The fan 31 is located directly below the bearing 30e and above the rotor 30b. The fan 31 rotates integrally with the motor shaft 30a, generating cooling air that flows from top to bottom inside the motor housing 12. As shown in Figure 4, exhaust ports 12a are provided on the left and right sides of the fastening portion 12b of the motor housing 12, penetrating both the inside and outside of the motor housing 12. The exhaust ports 12a are located at approximately the same vertical position as the fan 31. The upper end of the exhaust port 12a is formed by the lower surface of the fastened portion 14b of the gear housing 14.

[0046] As shown in Figure 12, the lower housing 11d houses the controller 35. The controller 35 primarily controls the drive of the motor 30. The controller 35 is provided with a control board housed in a shallow rectangular box-shaped case 35a. The case 35a is made of aluminum, for example, which has good thermal conductivity. The controller 35 is housed in the lower housing 11d with its longitudinal direction oriented vertically and the bottom surface (wide surface) of the case 35a positioned to the left. In this orientation, the longest side of the controller 35 extends vertically, and the shortest side extends horizontally. As shown in Figure 9, an air intake port 11i is provided on the lower left side of the lower housing 11d, penetrating the lower housing 11d inward and outward. The air intake port 11i is located opposite the right side of the magazine 80, with a gap in the horizontal direction.

[0047] As shown in Figure 5, a ventilation passage S is provided inside the lower housing 11d and the motor housing 12, through which cooling air flows from the intake port 11i to the exhaust port 12a. The ventilation passage S begins at the intake port 11i, where outside air flows in, and extends upward between the left inner surface of the lower housing 11d and the bottom outer surface (wide surface) of the controller 35 case 35a. At the connection point between the lower housing 11d and the motor housing 12, the ventilation passage S extends further upward toward the motor housing 12. When it reaches the fan 31, it is discharged to the outside from the exhaust port 12a radially outward of the fan 31. The cooling air flowing through the ventilation passage S cools the controller 35 and the motor 30.

[0048] <Deceleration mechanism 41> As shown in Figure 5, a reduction mechanism 41 is provided above the motor 30. In this embodiment, the reduction mechanism 41 reduces the output of the motor 30 in two stages: an upstream reduction section 41a and a downstream reduction section 41b. A drive bevel gear 42 is provided at the upper end of the motor shaft 30a. The drive bevel gear 42 is provided directly above the bearing 30e. This reduces the runout of the drive bevel gear 42 relative to the bearing 30e when the drive bevel gear 42 rotates around the motor axis J1. Therefore, the meshing accuracy of the drive bevel gear 42 can be maintained. A driven bevel gear 44 that meshes with the drive bevel gear 42 is provided to the upper right of the drive bevel gear 42. The drive bevel gear 42 and the driven bevel gear 44 constitute the upstream reduction section 41a.

[0049] As shown in Figure 5, the driven bevel gear 44 is integrally connected to the intermediate shaft 43. The intermediate shaft 43 extends in the left-right direction on the intermediate axis J2, which is perpendicular to the motor axis J1. The intermediate shaft 43 is rotatably supported around its axis by bearings 43a and 43b. Bearing 43a is connected to the right end of the intermediate shaft 43. Bearing 43a is inserted into a recess 14g provided on the left side of the cap 14a. The driven bevel gear 44 is located immediately to the left of bearing 43a. This reduces the runout of the driven bevel gear 44 relative to bearing 43a when the driven bevel gear 44 rotates around the axis of the intermediate axis J2. Therefore, the meshing accuracy of the driven bevel gear 44 can be maintained. Bearing 43b is connected to the left side of the intermediate shaft 43. Bearing 43b is press-fitted into a recess 14h provided on the inside (right side) of the left side of the gear housing 14.

[0050] As shown in Figure 5, a stopper 70 is provided approximately in the center of the intermediate shaft 43 in the left-right direction. The stopper 70 allows rotation of the intermediate shaft 43 in the forward direction and restricts rotation in the reverse direction. The stopper 70 will be described in detail later. The stopper 70 is provided to the left of the driven bevel gear 44 and immediately to the right of the bearing 43b of the bearing 43b. The stopper 70 overlaps the drive bevel gear 42 in the left-right direction on the extension of the motor axis J1 above the drive bevel gear 42. The stopper 70 overlaps the drive bevel gear 42 in the left-right direction for a length of more than half of the total left-right width of the stopper 70. A drive spur gear (downstream drive gear) 45 is provided at the left end of the intermediate shaft 43. The drive spur gear 45 is provided to the left of the bearing 43b. A stopper 70 and a drive bevel gear 42 are positioned between the driven bevel gear 44 and the drive spur gear 45 in the left-right direction. The intermediate shaft 43, the driven bevel gear 44, and the drive spur gear 45 rotate together around the axis of the intermediate shaft J2.

[0051] As shown in Figure 5, 14, a washer 70a is provided immediately to the right of the stopper 70. A washer 70b is provided immediately to the left of the stopper 70. In other words, the stopper 70 is sandwiched between the washers 70a and 70b on the left and right.

[0052] As shown in Figure 5, a driven spur gear 51 is provided rear and above the drive spur gear 45. The drive spur gear 45 and the driven spur gear 51 mesh together to form the downstream reduction section 41b. The driven spur gear 51 is the last driven gear in this disclosure, as it is the downstream reduction gear of the reduction mechanism. As shown in Figure 6, the driven spur gear 51 is rotatable around the axis of the lifter axis J3. The lifter axis J3 extends left and right parallel to the intermediate axis J2, rear and above the intermediate axis J2. The driven spur gear 51 is connected to the driving ring 52 via a buffer member 53. The driven spur gear 51, the driving ring 52, and the buffer member 53 constitute a buffer mechanism 50. The buffer mechanism 50 will be described in detail later. The driving ring 52 is rotatable integrally with the lifter shaft 61 around the axis of the lifter axis J3. Thus, the output of the motor 30 is reduced in the upstream reduction unit 41a and its rotational direction is changed, and it is further reduced in the downstream reduction unit 41b before being transmitted to the lifter shaft 61.

[0053] As shown in Figure 6, the lifter shaft 61 is rotatably supported around the axis of the lifter axis J3 by bearings 61e, 61f, and 61g. Bearing 61e is connected to the right end of the lifter shaft 61. Bearing 61e is inserted into a recess 14i provided on the outer (left) side of the left side of the gear housing 14. A driven spur gear 51 is positioned immediately to the left of bearing 61e. A washer 61h (see Figure 18) is interposed between bearing 61e and the driven spur gear 51. Bearing 61f is connected to the lifter shaft 61 approximately in the left-right direction of the lifter shaft 61, immediately to the left of the driven spur gear 51 and the driving ring 52. Bearing 61f is press-fitted into a recess 15c provided on the outer (right) side of the right side of the lifter housing 15. Bearing 61g is connected to the left end of the lifter shaft 61. The bearing 61g is inserted into a recess (not shown) on the right side of the cap 15a. A lifter 60 is provided between the bearing 61f and the bearing 61g in the left-right direction.

[0054] <Lifter 60> As shown in Figure 7, the lifter 60 is located above the driver 24. The front end of the lifter 60 is at approximately the same fore-aft position as the rear end of the magazine 80. The front end of the lifter housing 15 overlaps with the magazine 80 in the fore-aft direction. The rear end of the lifter 60 is located behind at least a portion of the operating surface 5a of the trigger 5. The lifter 60 has a wheel 62 and a plurality of engagement pins (engagement parts) 63. The wheel 62 rotates counterclockwise in Figure 7 as the lifter shaft 61 rotates around the axis of the lifter axis J3.

[0055] As shown in Figure 7, the multiple engagement pins 63 are arranged along the outer edge of the wheel 62. In this embodiment, five engagement pins 63 are arranged at approximately constant intervals in the circumferential direction of the wheel 62. The number of multiple engagement pins 63 is the same as the number of multiple rack teeth 24a provided on the driver 24. Each engagement pin 63 is cylindrical with its axial direction in the left-right direction. Each engagement pin 63 is held in the wheel 62 so as to be rotatable around its cylindrical axis. The multiple engagement pins 63 include a first engagement pin 63a and a final engagement pin 63b. The first engagement pin 63a is located at the front of the wheel 62 in the direction of rotation (counterclockwise in Figure 7). The final engagement pin 63b is located at the rear of the wheel 62 in the direction of rotation.

[0056] As shown in Figure 8, the first engagement pin 63a engages with the bottom surface (front) of the rearmost rack tooth 24a among the multiple rack teeth 24a during normal operation. The final engagement pin 63b engages with the bottom surface of the foremost rack tooth 24a among the multiple rack teeth 24a during normal operation. Each engagement pin 63 pushes the bottom surface of the engaged rack tooth 24a backward as the wheel 62 rotates counterclockwise as shown. This allows the driver 24 to move from bottom dead center to the rear standby position or top dead center against the gas pressure in the accumulator chamber 22.

[0057] For example, in the event of abnormal operation where the driver 24 is not driven to the bottom dead center due to a nail jam in the driving passage 2a, a mis-engagement may occur, such as the first engagement pin 63a engaging with the second rack tooth 24a from the rear. In such cases, the driver 24 can be moved to the bottom dead center in the next driving operation after the nail jam is cleared, thereby returning to the normal operating state where the first engagement pin 63a engages with the last rack tooth 24a.

[0058] As shown in Figure 7, the wheel 62 is fan-shaped when viewed from the left and right sides. The central angle of the fan shape of the wheel 62 is less than 180°. The outer diameter of the wheel 62 is set such that the central angle of the fan shape is less than 180°, and the circumferential distance from the first engagement pin 63a to the last engagement pin 63b corresponds to the longitudinal distance from the rearmost rack tooth 24a to the frontmost rack tooth 24a.

[0059] <Stoppa 70> As shown in Figure 15, the stopper 70 has a cylindrical outer ring 71 and a disc-shaped inner ring 72. The inner ring 72 is housed on the inner circumference side of the outer ring 71. The inner surface 71c of the outer ring 71 and the outer surface 72a of the inner ring 72 face each other with a small gap in the radial direction. The axial (left-right) widths of the outer ring 71 and the inner ring 72 are approximately the same.

[0060] As shown in Figure 15, the outer circumferential surface 71a of the outer ring 71 is provided with a plurality of protrusions 71b that project radially outward. The plurality of protrusions 71b are provided, for example, at intervals of approximately 60° in the circumferential direction of the outer circumferential surface 71a. As shown in Figure 16, the inside of the gear housing 14 is provided with a circular inner circumferential surface 14d when viewed from the left and right sides, and a plurality of grooves 14e recessed radially outward from the inner circumferential surface 14d. The inner circumferential surface 14d of the gear housing 14 faces the outer circumferential surface 71a of the outer ring 71 with a small gap in the radial direction. Each of the plurality of protrusions 71b of the outer ring 71 can be inserted into the plurality of grooves 14e of the gear housing 14. This prevents the outer ring 71 from rotating with respect to the axis of the intermediate axis J2 and holds it in the gear housing 14.

[0061] As shown in Figure 15, a spline groove 72b is provided at the radial center of the inner ring 72. A spline shaft 43c that engages with the spline groove 72b is provided on the outer circumference of the intermediate shaft 43. When the spline groove 72b and the spline shaft 43c engage, the inner ring 72 rotates around the axis together with the intermediate shaft 43.

[0062] As shown in Figure 15, the outer circumferential surface 72a of the inner ring 72 is provided with a plurality of wedge grooves 73. In this embodiment, six wedge grooves 73 are provided at approximately 60° intervals in the circumferential direction. A cylindrical wedge member 74 is inserted into each wedge groove 73. The axial length (left-right direction) of the wedge member 74 is approximately the same as the axial width of the outer ring 71 or the inner ring 72. The wedge member 74 is housed by left and right washers 70a and 70b to prevent it from coming out of the wedge groove 73.

[0063] As shown in Figure 16, the wedge groove 73 is recessed radially inward from the outer circumferential surface 72a of the inner ring 72 and extends circumferentially longer than the groove depth. Each wedge groove 73 is provided in substantially the same shape. The groove depth of the wedge groove 73 gradually decreases circumferentially toward the forward rotation direction R1. The rear part of the wedge groove 73 in the forward rotation direction R1 is a deep groove section 73a where the groove depth is greater than the diameter of the wedge member 74. The front part of the wedge groove 73 in the forward rotation direction R1 is a shallow groove section 73b where the groove depth is smaller than the diameter of the wedge member 74.

[0064] As shown in Figure 16, when the inner ring 72 rotates in the forward direction R1, each wedge member 74 moves towards the deep groove 73a within the wedge groove 73. As a result, a gap is created between each wedge member 74 and the inner circumferential surface 71c of the outer ring 71, or between each wedge member 74 and the bottom of the groove in the deep groove 73a. This allows the wedge members 74 to allow the rotation of the inner ring 72 in the forward direction R1 without hindering it. Thus, the intermediate shaft 43, driven bevel gear 44, and drive spur gear 45, which are integrated with the inner ring 72, are also allowed to rotate in the forward direction R1 (see Figure 5). When the inner ring 72 rotates in the forward direction R1, the lifter 60 rotates in the counterclockwise direction in Figure 7.

[0065] As shown in Figure 17, when the inner ring 72 attempts to rotate in the reverse direction R2, each wedge member 74 moves towards the shallow groove portion 73b within the wedge groove 73. As a result, each wedge member 74 is sandwiched between the inner circumferential surface 71c of the outer ring 71 and the shallow groove portion 73b of the wedge groove 73. For example, if there are three or more wedge members 74 sandwiched between the inner circumferential surface 71c of the outer ring 71 and the wedge groove 73, the rotation of the inner ring 72 in the reverse direction R2 is restricted. More specifically, the rotation of the inner ring 72 in the reverse direction R2 is restricted because the intermediate axis J2 is located inside the triangle formed by connecting the three sandwiched wedge members 74 in the left and right side views. When the inner ring 72 attempts to rotate in the reverse direction R2, the lifter 60 attempts to rotate in the reverse direction clockwise in Figure 7.

[0066] As shown in Figure 16, an elastic member 75 is interposed between the upper part of the outer circumferential surface 71a of the outer ring 71 and the inner circumferential surface 14d of the gear housing 14. The elastic member 75 is, for example, a cylindrical rubber member. The elastic member 75 biases the outer ring 71 downward. There is a dimensional tolerance for assembly between the outer circumferential surface 71a of the outer ring 71 and the inner circumferential surface 14d of the gear housing 14. This dimensional tolerance is used to slightly displace the outer ring 71 downward. The center 71d of the inner circumferential surface 71c of the outer ring 71 is located slightly below the intermediate axis J2, which is the rotation center of the inner ring 72. As a result, the radial distance from the bottom of each wedge groove 73 to the inner circumferential surface 71c of the outer ring 71 differs depending on the position. Specifically, the distance is slightly shorter for wedge grooves 73 located above the intermediate axis J2. The distance is slightly longer for wedge grooves 73 located below the intermediate axis J2.

[0067] The inner ring 72 normally rotates in the forward direction R1. Therefore, the wedge member 74 is generally located in the deep groove 73a. Lubricants such as grease are filled in the gear housing 14, for example, in the areas where the gears mesh. For example, grease may inadvertently enter the wedge groove 73 and harden. The wedge member 74, located in the deep groove 73a, may not be able to overcome the hardened grease, and its movement may be hindered when the inner ring 72 rotates in the reverse direction R2, causing it to move into the shallow groove 73b. Even in such a case, by biasing the outer ring 71 with the elastic member 75, there is always a wedge groove 73 with a short radial distance from the groove bottom to the inner circumferential surface 71c of the outer ring 71. Therefore, even if the movement of the wedge member 74 is hindered by grease, the wedge member 74 can be sandwiched between the groove bottom of the wedge groove 73 and the inner circumferential surface 71c of the outer ring 71. Thus, the wedge member 74 can more reliably restrict the rotation of the inner ring 72 in the reverse direction R2.

[0068] As shown in Figure 17, there is a time lag between when the inner ring 72 starts rotating in the reverse direction R2 and when the stopper 70 stops the inner ring 72. Therefore, the inner ring 72 rotates in the reverse direction R2 from the time it starts rotating in the reverse direction R2 until it stops. The rotation angle of the inner ring 72 until it stops is not a constant angle but has a range of variation. As shown in Figure 14, the stopper 70 is provided on the upstream side of the downstream reduction unit 41b. For example, if the reduction ratio in the downstream reduction unit 41b is 1 / 10, the rotation angle of the lifter shaft 61 from the time it starts to reverse until it stops is 1 / 10 of the rotation angle of the intermediate shaft 43, which is integrated with the inner ring 72, from the time it starts to reverse until it stops. The rotation angle of the lifter shaft 61 is proportional to the amount of movement of the driver 24 in the forward and backward direction. Thus, by providing the stopper 70 on the upstream side of the downstream reduction unit 41b, the amount of movement of the driver 24 in the forward and backward direction when the lifter 60 reverses can be shortened, and the error in the amount of movement can also be reduced.

[0069] As shown in Figure 5, the stopper 70 is provided downstream of the upstream reduction unit 41a. If only the reduction ratio is considered, it is preferable to provide the stopper upstream of the drive bevel gear 42. However, if the stopper is provided between the drive bevel gear 42 and the bearing 30e, the drive bevel gear 42 will be separated from the bearing 30e. Therefore, it is difficult to suppress the runout of the drive bevel gear 42 supported by the bearing 30e. Consequently, it is difficult to provide the stopper upstream of the drive bevel gear 42. Also, the driven bevel gear 44 is provided with a diameter greater than a predetermined value for the reduction ratio with respect to the drive bevel gear 42. Therefore, it is easy to secure space for a stopper or the like near the driven bevel gear 44. Thus, in this embodiment, the stopper 70 is provided downstream of the upstream reduction unit 41a and upstream of the downstream reduction unit 41b.

[0070] <Buffer mechanism 50> As shown in Figure 18, the buffer mechanism 50 has a driven spur gear 51 as an upstream rotating member and a driving ring 52 as a downstream rotating member. The right side of the driven spur gear 51 is a disc-shaped upstream disc portion 51a. The upstream disc portion 51a extends in a flat plate shape perpendicular to the left-right direction. The outer circumferential surface of the driven spur gear 51 extends cylindrically to the left from the upstream disc portion 51a. External teeth 51g that mesh with the drive spur gear 45 (see Figure 14) are provided on the outer circumferential surface of the driven spur gear 51. A recess 51b opening to the left is provided on the inner side of the outer circumferential surface of the driven spur gear 51. A circular hole 51f is provided in the radial center of the driven spur gear 51, penetrating the upstream disc portion 51a in the left-right direction. The lifter shaft 61 is inserted through the hole 51f.

[0071] As shown in Figure 18, the recess 51b of the driven spur gear 51 is provided with a plurality of upstream protrusions 51c that extend to the left from the upstream disc portion 51a. In this embodiment, three upstream protrusions 51c are provided at intervals of approximately 120° in the circumferential direction. The upstream protrusions 51c are fan-shaped when viewed from the left and right sides. The left end surface of the upstream protrusion 51c is planar and parallel to the upstream disc portion 51a. The left end surface of the upstream protrusion 51c is located to the right of the left end of the entire driven spur gear 51, specifically by a length approximately the same as the thickness of the downstream disc portion 52a, which will be described later. When the driven spur gear 51, the buffer member 53, and the driving ring 52 are assembled, at least a part of the downstream disc portion 52a is housed in the recess 51b of the driven spur gear 51, and preferably the entire downstream disc portion 52a is housed in the recess 51b.

[0072] As shown in Figure 18, the upstream protrusion 51c has an upstream side surface 51d that is forward in the forward rotation direction R3 (see Figure 20) and an upstream inclined side surface 51e that is rearward in the forward rotation direction R3. The upstream side surface 51d and the upstream inclined side surface 51e extend radially in a planar manner between the outer circumferential surface of the driven spur gear 51 and the hole 51f. The upstream side surface 51d is perpendicular to the upstream disc portion 51a. The upstream inclined side surface 51e inclines towards the rearward in the forward rotation direction R3 as it approaches the upstream disc portion 51a from left to right. The upstream inclined side surface 51e inclines with respect to the upstream disc portion 51a at an inclination angle of, for example, 30° to 60°.

[0073] As shown in Figure 19, the left side of the driving ring 52 is a disc-shaped downstream disc portion 52a. The downstream disc portion 52a extends in a flat shape perpendicular to the left-right direction. A circular hole 52e is provided in the radial center of the driving ring 52, penetrating the downstream disc portion 52a in the left-right direction. The lifter shaft 61 is inserted through the hole 52e. The driving ring 52 has a plurality of downstream protrusions 52b that extend to the right from the downstream disc portion 52a. In this embodiment, three downstream protrusions 52b are provided at approximately 120° intervals in the circumferential direction. The downstream protrusions 52b are fan-shaped when viewed from the left and right sides. The right end surface of the downstream protrusions 52b is planar and parallel to the downstream disc portion 52a.

[0074] As shown in Figure 19, the downstream protrusion 52b has a downstream inclined side surface 52d that is forward in the forward rotation direction R3 (see Figure 20) and a downstream side surface 52c that is rearward in the forward rotation direction R3. The downstream side surface 52c and the downstream inclined side surface 52d extend radially in a planar manner from the hole 52e of the driving ring 52 to the outer edge. The downstream side surface 52c is perpendicular to the downstream disc portion 52a. The downstream inclined side surface 52d inclins towards the rearward direction R3 as it approaches the downstream disc portion 52a from right to left. The downstream inclined side surface 52d inclins with respect to the downstream disc portion 52a at approximately the same inclination angle as the upstream inclined side surface 51e.

[0075] As shown in Figures 18 and 19, the driving ring 52 is provided with a plurality of ball grooves 52f that communicate with the hole 52e. The plurality of ball grooves 52f are provided on the inner periphery of each downstream projection 52b, for a total of three grooves. The ball grooves 52f extend from the left side of the downstream disc portion 52a toward the right. The opening side (left side) of the ball groove 52f is cylindrical, and the inner surface of the bottom side (right side) is spherical. The groove depth in the left-right direction of each ball groove 52f is approximately constant.

[0076] As shown in Figure 18, the cushioning mechanism 50 is provided with three cushioning members 53. The cushioning members 53 are made of, for example, highly elastic rubber. The cushioning members 53 are each provided in substantially the same shape. The cushioning members 53 are fan-shaped when viewed from the left and right sides. The outer circumferential surface of the cushioning member 53 faces radially opposite the inner circumferential surface of the recess 51b of the driven spur gear 51. The inner circumferential surface of the cushioning member 53 faces radially opposite the outer circumferential surface 61i of the lifter shaft 61. The thickness of the cushioning member 53 in the left-right direction is substantially constant, except for the protrusion 53c which will be described later.

[0077] As shown in Figure 20, the cushioning member 53 has a second side surface 53b facing forward in the forward rotation direction R3 and a first side surface 53a facing backward in the forward rotation direction R3. The first side surface 53a and the second side surface 53b extend planarly in the left-right direction. The first side surface 53a and the second side surface 53b are perpendicular to the upstream disc portion 51a or the downstream disc portion 52a. The positional relationship between the first side surface 53a and the second side surface 53b is based on the state in which the cushioning member 53 is assembled between the driven spur gear 51 and the driving ring 52. Since the cushioning member 53 has a symmetrical shape before assembly, it can be assembled between the driven spur gear 51 and the driving ring 52 without any problems even if, for example, the first side surface 53a and the second side surface 53b shown are reversed.

[0078] As shown in Figures 18 and 19, protrusions 53c are provided in the center of both the left and right sides of the cushioning member 53. The protrusions 53c extend spherically outward from the cushioning member 53 to the left and right. The protrusions 53c are circular in shape when viewed from the left and right sides. The right protrusion 53c elastically contacts the left side surface of the upstream disc portion 51a. The left protrusion 53c elastically contacts the right side surface of the downstream disc portion 52a. As shown in Figure 6, the cushioning member 53 is sandwiched between the upstream disc portion 51a and the downstream disc portion 52a in the left-right direction. The cushioning member 53 is contained within the left-right width of the driven spur gear 51.

[0079] As shown in Figure 20, the cushioning member 53 is housed between the upstream protrusion 51c and the downstream protrusion 52b in the circumferential direction. The first side surface 53a of the cushioning member 53 elastically contacts the upstream side surface 51d of the driven spur gear 51 in the circumferential direction. The second side surface 53b of the cushioning member 53 elastically contacts the downstream side surface 52c of the driving ring 52 in the circumferential direction. As shown in Figure 18, the upstream inclined side surface 51e of the driven spur gear 51 and the downstream inclined side surface 52d of the driving ring 52 face each other during assembly.

[0080] By providing an upstream inclined side surface 51e of the driven spur gear 51 and a downstream inclined side surface 52d of the driving ring 52, it is possible to prevent the cushioning member 53 from being housed in the wrong position. For example, even if one tries to house the cushioning member 53 between the upstream inclined side surface 51e and the downstream inclined side surface 52d, the upstream inclined side surface 51e and the downstream inclined side surface 52d are inclined with respect to the respective outer surfaces of the cushioning member 53. Therefore, it is not possible to house the cushioning member 53 between the upstream inclined side surface 51e and the downstream inclined side surface 52d and assemble it correctly. Furthermore, during assembly, for example, the driven spur gear 51 is rotated in the forward direction R3 relative to the driving ring 52 to bring the upstream inclined side surface 51e closer to the downstream inclined side surface 52d in the circumferential direction. This causes the upstream side surface 51d to push the first side surface 53a of the cushioning member 53 in the circumferential direction, allowing the cushioning member 53 to be assembled while being moved to the correct position.

[0081] As shown in Figure 6, the lifter shaft 61 is provided as a single shaft member by connecting the left shaft body 61a and the right shaft sleeve 61b. The wheel 62 is connected to the shaft body 61a. The cushioning mechanism 50 is connected to the shaft sleeve 61b. A spline groove 61c is provided at the radial center of the shaft sleeve 61b, which engages with the spline shaft of the shaft body 61a.

[0082] As shown in Figure 20, the outer circumferential surface 61i of the shaft sleeve 61b is provided with a total of three ball holes 61d at approximately 120° intervals in the circumferential direction. The ball holes 61d are recessed in a hemispherical shape toward the radially inward direction. A metal ball 54 is inserted into each ball hole 61d. The hemispherical portion of the ball 54 protruding radially outward from the ball hole 61d is inserted into the ball groove 52f of the driving ring 52. In this way, the driving ring 52 is integrally connected to the shaft sleeve 61b via the balls 54. The driving ring 52 can rotate integrally with the lifter shaft 61 around the axis of the lifter axis J3.

[0083] As shown in Figure 20, the driven spur gear 51 rotates in the forward direction R3 around the axis of the lifter axis J3 by receiving power from the drive spur gear 45. At this time, first the upstream side surface 51d of the driven spur gear 51 elastically presses the first side surface 53a of the buffer member 53 in the forward direction R3. Furthermore, the second side surface 53b of the buffer member 53 elastically presses the downstream side surface 52c of the driving ring 52 in the forward direction R3. As a result, the driving ring 52 rotates in the forward direction R3 around the axis of the lifter axis J3 together with the lifter shaft 61. Thus, the lifter 60 rotates in the forward direction in the counterclockwise direction in Figure 7.

[0084] As shown in Figure 20, the driving ring 52 may attempt to rotate in the reverse direction R4 together with the lifter shaft 61. When the driver 24 is moved backward or when the impact of the driver 24's driving motion is transmitted to the lifter 60, the lifter shaft 61 may reverse direction (see Figure 7). Also, for example, if the lifter 60 and driver 24 are misaligned, the engagement pin 63 of the lifter 60 may come into contact with the rack teeth 24a of the driver 24 as it moves forward, causing the lifter shaft 61 to reverse direction. At this time, first the downstream side surface 52c of the driving ring 52 elastically pushes the second side surface 53b of the cushioning member 53 in the reverse direction R4. Furthermore, the first side surface 53a of the cushioning member 53 elastically pushes the upstream side 51d of the driven spur gear 51 in the reverse direction R4. As a result, the impact on the driving ring 52 side is reduced by the cushioning member 53, and the transmission of impact to the driven spur gear 51 and its upstream side can be suppressed. Since the driven spur gear 51 is the downstream reduction gear of the reduction mechanism 41, the shock absorber 50 can suppress the transmission of the lifter 60 to all the reduction gears of the reduction mechanism 41.

[0085] <Magazine 80> As shown in Figure 1, a roughly rectangular box-shaped magazine 80 is provided below the driving nose section 2. The magazine 80 extends straight downward from the driver guide 16. The magazine 80 is connected to the driver guide 16 at its upper part 80a. The magazine 80 is connected to the lower housing 11d at its lower part 80b. The magazine 80 is mainly made of metal and has high rigidity. Therefore, the mechanism section 13 (see Figure 7) and the lower housing 11d are connected vertically not only via the motor housing 12 but also via the magazine 80.

[0086] As shown in Figure 2, the magazine 80 is loaded with multiple driving tools N arranged in parallel in the vertical direction. The driving tools N are loaded into the magazine 80 in a position where the head Na is located at the rear end, and a pair of legs Nb extend forward from both the left and right ends of the head Na. The magazine 80 is provided with a pusher 81 that supplies the driving tools N to the upper driving passage 2a. The pusher surface 81a at the upper end of the pusher 81 biases the multiple driving tools N upward. The pusher 81 has a coil spring 81c as a biasing member that biases them upward.

[0087] As shown in Figure 3, the magazine 80 is provided with two rails 80c, one in the front and one in the back, that extend straight in the vertical direction. The upper part of the rear rail 80c is provided as a bulge 80d that extends in the left-right direction. The head Na of the driving tool N is inserted through the bulge 80d, thereby being held in place so that it does not fall out, for example, from the rear of the magazine 80. As shown in Figure 10, the pusher 81 has a rail engaging portion 81b that engages with the rail 80c. The pusher 81 is slidable in the vertical direction along the rail 80c.

[0088] As shown in Figure 1, a release lever 81d is provided at the front of the pusher 81. The release lever 81d can be pushed backward with a finger. A box-shaped recess 81f is provided at the bottom of the pusher 81. The recess 81f opens to the left and is enclosed on the front, back, top, bottom, and right side by walls. The user can push the release lever 81d with one finger while hooking another finger into the recess 81f. This allows the user to push the release lever 81d and slide the pusher 81 up and down with one hand.

[0089] As shown in Figures 1 and 8, a claw 81e is provided, which is integrated with the release lever 81d. The claw 81e protrudes forward. The claw 81e and the release lever 81d are biased forward by a biasing member (not shown). When the release lever 81d is pushed backward, the claw 81e also moves backward. A claw engagement portion 80e is provided at the front end of the lower part 80b of the magazine 80. The claw engagement portion 80e is pin-shaped and extends in the left-right direction, and releasably engages with the claw 81e. When the claw 81e engages with the claw engagement portion 80e, the pusher 81 is held in its lowest position.

[0090] As shown in Figure 1, a recess 11h is provided on the left side of the lower housing 11d. The upper end height of the recess 11h is lower than that of the right side of the lower housing 11d, which is connected to the motor housing 12. The recess 11h is located behind the magazine 80. As shown in Figure 3, the upper end surface of the recess 11h is approximately horizontal and lower than the pusher surface 81a of the pusher 81 at its lowest position. Therefore, a space is provided behind the magazine 80 and above the recess 11h for loading the driving tool N into the magazine 80. With the pusher 81 held at its lowest position, a linked driving tool consisting of multiple driving tools N can be loaded from the rear end of the magazine 80 toward the front. After placing the linked driving tool on the pusher surface 81a, the engagement between the claw 81e and the claw engagement portion 80e is released (see Figure 8). This pushes the linked driving tool upward by the pusher 81, allowing it to be loaded into the magazine 80.

[0091] As shown in Figure 3, a removal lever 80f is provided on the left side of the lower part 80b of the magazine 80. By pressing the removal lever 80f and moving the magazine 80 forward and downward, the lower part 80b of the magazine 80 can be removed from the lower housing 11d. When attaching the lower part 80b of the magazine 80 to the lower housing 11d, it is automatically attached by bringing the lower part 80b of the magazine 80 closer to the lower housing 11d with the rear and upward direction, without pressing the removal lever 80f.

[0092] Next, the sequence of operations of the driving tool 1 will be explained with reference to Figures 1 to 20. The driver 24 in the standby position is stopped slightly in front of the top dead center (see Figure 8). When the driver 24 is in the standby position, the bottom surface of the foremost rack tooth 24a is engaged with the final engagement pin 63b. The contact arm 3 moves backward when pressed against the material to be driven W. The adjuster 6 moves backward together with the contact arm 3 and presses the switch 6c. The switch 6c sends an ON signal to the controller 35. The controller 35 starts the motor 30 when it receives the ON signal from the switch 6c and the trigger 5 is pushed backward. When the motor 30 is started, the wheel 62 of the lifter 60 rotates. The final engagement pin 63b moves the foremost rack tooth 24a backward. This moves the driver 24 backward from the standby position to the top dead center.

[0093] When the driver 24 is stopped in the standby position, the tip 24b of the driver 24 and the head Na of the driving tool N closest to the driving passage 2a overlap in the front-to-back direction. Therefore, no driving tools N are yet loaded into the driving passage 2a. When the tip 24b of the driver 24 moves behind the head Na of the driving tool N, the uppermost driving tool N is loaded into the driving passage 2a. When the driver 24 moves to top dead center and reaches the state just before driving, the final engagement pin 63b detaches upward from the bottom surface of the foremost rack teeth 24a. The driver 24 moves forward, biased by the gas pressure in the accumulator chamber 22 that was applied to the piston 23. The tip 24b of the driver 24 strikes the driving tool N in the driving passage 2a forward. The struck driving tool N is ejected from the nozzle 2b into the material to be driven W.

[0094] The wheel 62 continues to rotate while the driver 24 is moving forward and even after it reaches bottom dead center. After the driver 24 reaches bottom dead center, when the wheel 62 has rotated to a predetermined rotation angle, the first engagement pin 63a engages with the bottom surface of the rearmost rack tooth 24a. This initiates a return operation that moves the driver 24 to a rearward standby position. When the final engagement pin 63b engages with the bottom surface of the foremost rack tooth 24a, the driver 24 returns to the standby position. For example, by appropriately measuring the time from the start of motor 30 operation, or by appropriately measuring the rotation position of the wheel 62, the motor 30 is stopped when the piston 23 reaches the standby position. This holds the driver 24 in the standby position. This completes the series of driving operations.

[0095] As described above, the driving tool 1 has a driving mechanism 20, a power transmission mechanism 40, and a mechanism housing (gear housing 14, lifter housing 15) as shown in Figures 4, 7, 11, and 12. The driving mechanism 20 biases the driver 24 forward. The power transmission mechanism 40 moves the driver 24 backward by the output of the motor 30. The gear housing 14 and lifter housing 15 house the power transmission mechanism 40. The driving tool 1 has a motor housing 12, a fastening part 12b, and a main body housing 11. The motor housing 12 houses the motor 30. The fastening part 12b screws the motor housing 12 to the gear housing 14. The main body housing 11 covers the gear housing 14 and the lifter housing 15 and exposes the motor housing 12.

[0096] Therefore, the gear housing 14, which rotatably supports the motor shaft 30a and rotor 30b, and the motor housing 12, which supports the stator 30c, are fastened together with screws. As a result, the motor housing 12 follows vibrations generated in the power transmission mechanism 40 within the gear housing 14 or the lifter housing 15. This makes it possible to make the vibrations transmitted from the gear housing 14 to the rotor 30b and the vibrations transmitted from the gear housing 14 to the stator 30c via the motor housing 12 the same vibration mode. Therefore, contact between the rotor 30b and the stator 30c due to vibration transmission can be suppressed. In this way, contact between the rotor 30b and the stator 30c of the motor 30 can be suppressed and core friction can be prevented.

[0097] Furthermore, by exposing the motor housing 12 from the main body housing 11, the size of the motor housing 12 can be suppressed. This increases the flexibility of the arrangement of structures near the motor housing 12, such as the magazine 80 and the handle 4, and makes the entire driving tool 1 more compact.

[0098] As shown in Figures 4 and 11, the motor housing 12 is cylindrical. The cylindrical fastened portion 14b of the gear housing 14, to which the fastening portion 12b is screw-fastened, is exposed from the main housing 11. Therefore, the transmission of vibrations from the gear housing 14 to the motor housing 12 via the main housing 11 can be further suppressed. In addition, the compactness of the area around the motor housing 12 can be further improved. Furthermore, by fastening the cylindrical motor housing 12 to the cylindrical fastened portion 14b, the airtightness and rigidity of the motor housing 12 and gear housing 14 can be maintained at the same level as in conventional structures while making it compact.

[0099] As shown in Figures 11 and 12, the main housing 11 has an upper housing 11a, a handle housing 11b, and a lower housing 11d. The upper housing 11a houses the gear housing 14 and the lifter housing 15. The handle housing 11b extends downward from the upper housing 11a and is responsible for the handle 4. The lower housing 11d protrudes forward from below the handle housing 11b and is connected to the lower part of the motor housing 12.

[0100] For example, consider the case where vibration is transmitted from the gear housing 14 or lifter housing 15 to the lower part of the motor housing 12 via the main housing 11. The upper housing 11a, handle housing 11b, and lower housing 11d are interposed in this vibration transmission path. The main housing 11 is made of a material with lower rigidity than the motor housing 12, etc. If vibration is transmitted through this transmission path, the handle housing 11b will bend primarily. As a result, the vibration is reduced before it is transmitted to the lower housing 11d. This suppresses the transmission of vibration to the motor housing 12 via the main housing 11. Thus, it is possible to suppress the transmission of vibration to the motor housing 12 from sources other than the gear housing 14. This allows the vibration modes of the rotor 30b and stator 30c to be more matched, and core friction can be suppressed.

[0101] As shown in Figures 5 and 6, a rubber ring (elastic member) 18 is provided interposed between the upper housing 11a and the gear housing 14 or lifter housing 15. Therefore, by absorbing vibrations with the rubber ring 18, vibrations transmitted from the gear housing 14 or lifter housing 15 to the upper housing 11a can be efficiently reduced.

[0102] As shown in Figures 12 and 13, the elastic member 18 is a rubber ring that is held in an elastically deformed state between the outer surface of the gear housing 14 or lifter housing 15 and the inner surface of the upper housing 11a. Therefore, the gear housing 14 or lifter housing 15 and the upper housing 11a are connected with the rubber ring in between over a wide range corresponding to the diameter of the rubber ring. This suppresses the transmission of vibrations from the gear housing 14 or lifter housing 15 to the main housing 11, while increasing the stability with which the main housing 11 holds the gear housing 14 and the lifter housing 15.

[0103] As shown in Figures 12 and 13, the lower housing 11d has a connecting portion 11g. The connecting portion 11g is connected to the lower part of the motor housing 12 and positions the lower part of the motor housing 12 (connected portion 12c). Therefore, the lower part of the motor housing 12 and the connecting portion 11g of the lower housing 11d are connected and positioned relative to each other without the need for, for example, an elastic member. As a result, the motor housing 12 is screw-fastened to the gear housing 14 at the top and connected to the lower housing 11d at the bottom, and is positioned in the vertical direction. This allows the motor housing 12 to be held stably.

[0104] As shown in Figures 5 and 12, a controller 35 is provided to control the motor 30. The controller 35 is housed in the lower housing 11d. Therefore, by placing the controller 35 near the motor 30, the wiring connecting the two can be made more compact. Moreover, the controller 35 can be compactly positioned by utilizing the space below the motor 30.

[0105] As shown in Figure 5, the driving tool 1 has a fan 31, an air intake 11i, and a ventilation passage S. The fan 31 rotates driven by the motor 30. The air intake 11i is formed at the bottom of the lower housing 11d. The ventilation passage S introduces outside air, drawn in by the suction force of the fan 31 from the air intake 11i, into the motor housing 12 from inside the lower housing 11d. Therefore, the controller 35 can also be cooled using the cooling air that cools the motor 30. Furthermore, by making the ventilation passage S a simple path with few detours, the force of the cooling airflow can be maintained from the air intake 11i to the exhaust port 12a.

[0106] As shown in Figures 5 and 12, the controller 35 is rectangular in shape and is housed in the lower housing 11d with its longitudinal direction extending vertically. Outside air from the intake port 11i flows along the longitudinal direction of the controller 35. Therefore, by directing the cooling air along the longitudinal direction of the controller 35, the controller 35 can be cooled efficiently.

[0107] As shown in Figure 11, a magazine 80 is provided to house multiple driving tools N. The upper part 80a of the magazine 80 is connected to the gear housing 14 and the lifter housing 15. The lower part 80b of the magazine 80 is connected to the lower housing 11d. Therefore, the magazine 80 is positioned vertically by being connected to the gear housing 14 and the lifter housing 15 at the upper part 80a and to the lower housing 11d at the lower part 80b. This allows the magazine 80 to be held stably.

[0108] Various modifications can be made to the driving tool 1 of this embodiment described above. A gas spring type driving tool was given as an example of the driving tool. Alternatively, the present disclosure may be applied to, for example, a mechanical spring type driving tool. Staples were given as an example of the driving tool N. Alternatively, the present disclosure may be applied to, for example, a driving tool capable of driving nails as the driving tool N.

[0109] An example is shown of a lifter 60 positioned above the driver 24. An example is shown of a reduction mechanism 41 from the motor 30 to the lifter 60, which includes a bevel gear and a spur gear. The lifter 60 may be positioned on either the left or right side of the driver 24 instead of the example shown. The reduction mechanism 41 may also include, for example, a planetary gear reduction mechanism.

[0110] An example shows a motor housing 12 positioned to the right of the magazine 80. Alternatively, the motor housing may be positioned to the left of the magazine. An example shows a magazine 80 extending straight downward from the drive-in nose section 2. Alternatively, the magazine 80 may be tilted, for example, downward in the left-right direction.

[0111] An example configuration is shown in which the motor housing 12 is sandwiched and connected from both sides by the halved lower housing 11d. Alternatively, for example, the lower housing 11d and the motor housing 12 may be directly fastened together with screws. An example is shown of an exhaust port 12a passing through the motor housing 12. Alternatively, for example, an exhaust port may be provided in the fastened portion 14b of the gear housing 14.

[0112] An example is shown of a controller 35 housed in the lower housing 11d below the motor housing 12. The example shows the controller 35 housed in the lower housing 11d with its longitudinal direction being vertical. The arrangement and orientation of the controller 35 are not limited to the example shown and can be changed as appropriate. For example, the longitudinal direction of the controller 35 may be inclined relative to the front-to-back direction or the vertical direction.

[0113] An example of a rubber ring 18 interposed between the inner surface of the upper housing 11a and the outer surface of the mechanism housing is shown. The position and number of rubber rings 18 are not limited to the example position and may be changed as appropriate. Alternatively, a spring may be used instead of the rubber rings 18.

[0114] A reduction mechanism 41 that reduces speed in two stages, an upstream reduction section 41a and a downstream reduction section 41b, is illustrated. It is illustrated that the upstream reduction section 41a is composed of meshing bevel gears, and the downstream reduction section 41b is composed of meshing spur gears. The number of reduction stages, the type of gears, the order, etc., are not limited to those illustrated and can be changed as appropriate. For example, there may be only one reduction stage, or three or more reduction stages. Instead of meshing spur gears, a reduction section with meshing helical gears may be used. For example, the upstream reduction section may be meshing spur gears or helical gears, and the downstream reduction section may be meshing bevel gears. For example, in the case of a three-stage reduction, the first stage may be meshing bevel gears, and the second and third stages may be meshing spur gears or helical gears. Alternatively, the first and third stages may be meshing spur gears or helical gears, and the second stage may be meshing bevel gears, etc.

[0115] An example is shown of a stopper 70 provided on the outer circumference of the intermediate shaft 43, downstream of the driven bevel gear 44 and upstream of the drive spur gear 45. The position of the stopper 70 is not limited to this. For example, the stopper 70 may be provided on the outer circumference of the lifter shaft 61. For example, a drive spur gear or drive helical gear may be provided at the downstream end of the motor shaft 30a, and the stopper 70 may be provided on the outer circumference of the motor shaft 30a. For example, if the reduction mechanism has three or more stages, the stopper 70 may be provided on the outer circumference of any rotating member downstream of the driven bevel gear.

[0116] An example of a stopper 70 having six wedge grooves 73 and six wedge members 74 is shown. The number of wedge grooves 73 and wedge members 74 is not limited to this and may be changed as appropriate. An example of a wedge groove 73 provided on the outer circumferential surface 72a of the inner ring 72 is shown. Alternatively, a wedge groove 73 may be provided on the inner circumferential surface 71c of the outer ring 71, recessed radially outward.

[0117] An example of a buffer mechanism 50 including a driven spur gear 51 is provided on the outer circumference of the lifter shaft 61. The position and configuration of the buffer mechanism 50 are not limited to this example. For example, the upstream rotating member does not also serve as a reduction gear, and the buffer mechanism 50 may be provided on the outer circumference of the lifter shaft 61 downstream of the driven spur gear 51. For example, the buffer mechanism 50 may be provided upstream of the furthest downstream reduction gear, for example, on the outer circumference of the intermediate shaft 43.

[0118] An example is given of a configuration in which the lifter shaft 61 and the driving ring 52 are rotatably connected as a single unit by a ball 54. Alternatively, the lifter shaft 61 and the driving ring 52 may be rotatably connected as a single unit by, for example, a spline shaft fitting. An example is given of a configuration in which a hemispherical ball hole 61d is provided in the lifter shaft 61 and a ball groove 52f extending in the axial direction is provided in the driving ring 52. Alternatively, for example, a configuration may be provided in which ball grooves extending in the axial direction are provided in both the lifter shaft 61 and the driving ring 52, and the ball 54 is positioned in the axial direction at the bottom of both ball grooves. An example is given of a cushioning mechanism 50 having three cushioning members 53. The number of cushioning members 53 is not limited to this and may be changed as appropriate. [Explanation of Symbols]

[0119] 1… Driving tool 2...Injection nose section, 2a...Injection passage, 2b...Exjection port 3... Contact arm, 3a... Adjuster connection part 4…Handle 5...Trigger, 5a...Operating surface, 5b...Trigger switch 6...Adjuster, 6a...Rotating shaft, 6b...Compression spring, 6c...Switch 7…Battery mounting section 8…Battery 10...Tool body 11...Main housing, 11a...Upper housing, 11b...Handle housing 11c... Widening section, 11d... Lower housing, 11e... Right housing, 11f...Left housing, 11g...Connecting part, 11h...Recess, 11i...Air intake 12...Motor housing, 12a...Exhaust port, 12b...Fastening part, 12c...Connected part 12d…recess 13... Mechanism section 14...Gear housing (mechanism housing), 14a...Cap, 14b...Fastened part 14c...Ring holding part, 14d...Inner circumferential surface, 14e...Groove 14f, 14g, 14h, 14i…recessed 15... Lifter housing (mechanism housing), 15a... Cap, 15b... Ring retaining part 15c, 15d…recessed 16…Driver Guide 17... Bolt 18…Rubber ring (elastic material) 20…Driving mechanism 21...Cylinder, 21a...Front end 22...Pressure accumulation chamber, 22a...Air chamber 23... Piston 24...Driver, 24a...Rack teeth (engaged part), 24b...Tip 25...Cushion, 25a...Front end 30...motor, 30a...motor shaft, 30b...rotor, 30c...stator 30d, 30e…bearings 31…fan 35...Controller, 35a...Case 40…Power transmission mechanism 41...Reduction mechanism, 41a...Upstream reduction section, 41b...Downstream reduction section 42... Drive bevel gear 43...Intermediate shaft (rotating member), 43a, 43b...Bearing, 43c...Spline shaft 44... Driven bevel gear 45…Drive spur gear 50…Buffer mechanism 51...Driven spur gear (upstream rotating member, final driven gear), 51a...Upstream disc section 51b…recess, 51c…upstream protrusion, 51d…upstream side surface, 51e…upstream inclined side surface 51f…hole, 51g…external tooth 52...Driving ring (downstream rotating member), 52a...Downstream disc portion, 52b...Downstream protrusion portion 52c…downstream side, 52d…downstream inclined side, 52e…hole (inner surface), 52f…ball groove 53...cushioning member, 53a...first side surface, 53b...second side surface, 53c...protrusion 54... Ball 60... Lifter 61... Lifter shaft, 61a... Shaft body, 61b... Shaft sleeve, 61c... Spline groove 61d…Ball hole, 61e, 61f, 61g…Bearing, 61h…Washer, 61i…Outer surface 62... Wheels 63...Engaging pin (engaging part), 63a...First engaging pin, 63b...Final engaging pin 70... Stopper, 70a, 70b... Washer 71...Outer ring, 71a...Outer circumference, 71b...Protrusion, 71c...Inner circumference, 71d...Center 72...Inner ring, 72a...Outer surface, 72b...Spline groove 73...Wedge groove, 73a...Deep groove section, 73b...Shallow groove section 74... Wedge member 75...Elastic member 80...Magazine, 80a...Upper part, 80b...Lower part, 80c...Rail, 80d...Bulge 80e... Claw engagement part, 80f... Removal lever 81...Pusher, 81a...Pusher surface, 81b...Rail engagement part, 81c...Spring 81d...Lock release lever, 81e...Claw, 81f...Recess N...Drilling tool, Na...Head, Nb...Legs W... material to be driven in J1…Motor axis, J2…Intermediate axis (center of rotation), J3…Lifter axis R1, R3…Forward rotation direction, R2, R4…Reverse rotation direction A... Gap S... Ventilation channel

Claims

1. It is a driving tool, A driving mechanism that biases the driver forward, A power transmission mechanism that moves the driver backward by the output of the motor, A mechanism housing that accommodates the power transmission mechanism, A motor housing that houses the motor, A fastening portion for screw fastening the motor housing to the mechanism housing, A driving tool having a main body housing that covers the mechanism housing and exposes the motor housing.

2. The driving tool according to claim 1, The motor housing is cylindrical, A driving tool in which the cylindrical fastened portion of the mechanism housing to which the fastening portion is screw-fastened is exposed from the main housing.

3. A driving tool according to claim 1 or 2, The main body housing comprises an upper housing that houses the mechanism housing, a handle housing that extends downward from the upper housing and is responsible for the handle, and a lower housing that protrudes forward from the lower part of the handle housing and is connected to the lower part of the motor housing, making it a driving tool.

4. The driving tool according to claim 3, A driving tool having an elastic member interposed between the upper housing and the mechanism housing.

5. The driving tool according to claim 4, The aforementioned elastic member is a rubber ring held in an elastically deformed state between the outer surface of the mechanism housing and the inner surface of the upper housing, which is used as a driving tool.

6. A driving tool according to any one of claims 3 to 5, The lower housing is a driving tool having a connecting portion that is connected to the lower part of the motor housing and positions the lower part of the motor housing.

7. A driving tool according to any one of claims 3 to 6, The motor has a controller, A driving tool in which the controller is housed in the lower housing.

8. The driving tool according to claim 7, A fan that rotates by the drive of the aforementioned motor, An air intake port formed at the lower part of the lower housing, A driving tool having a ventilation passage that introduces outside air, taken in from the air intake by the suction force of the fan, into the motor housing from inside the lower housing.

9. The driving tool according to claim 8, It has a magazine that houses multiple of the aforementioned driving tools and is long in the front-to-back and up-to-down directions, The controller is rectangular in shape and is housed in the lower housing with a wide surface extending in the longitudinal direction aligned with the magazine. A driving tool in which outside air from the intake port flows between the inner surface of the lower housing and the wide surface in the left-right direction between the controller and the magazine.

10. A driving tool according to any one of claims 3 to 9, It has a magazine that houses multiple of the aforementioned driving tools, The upper part of the magazine is connected to the mechanism housing, A driving tool in which the lower part of the magazine is connected to the lower housing.

Images