JP7457623B2 - Attachment and tool system for impact rotary tool - Google Patents

Description

The present disclosure generally relates to an impact rotary tool attachment and a tool system, and more particularly to an impact rotary tool attachment to which rotational driving force is transmitted from an impact rotary tool, and a tool system including the impact rotary tool attachment.

Patent Document 1 describes an attachment for an impact rotary tool that measures the torque applied to a shaft portion that transmits the impact force generated by the impact rotary tool to a tip tool.

JP 2015-020243 A

There is a demand for an attachment for an impact rotary tool that can be easily removed from the impact rotary tool.

The present disclosure has been made in view of the above reasons, and an object thereof is to provide an attachment for an impact rotary tool and a tool system that can be easily removed from the impact rotary tool.

In order to solve the above problems, an impact rotary tool attachment according to one aspect of the present disclosure is an impact rotary tool attachment that is attached to an impact rotary tool. The impact rotary tool attachment includes a connecting shaft and an input shaft. The connecting shaft is inserted into an insertion port of the impact rotary tool and faces each of the plurality of spherical bodies of the impact rotary tool, and a rotational driving force from the impact rotary tool is transmitted to the input shaft. The input shaft transmits a rotational driving force from the impact rotary tool via the connecting shaft. The connecting shaft has an input portion and an output portion. The input portion is a portion on the side where a rotational driving force is transmitted from the impact rotary tool in the axial direction of the connecting shaft. The output portion extends from the input portion along the axial direction and is a portion on the side where a rotational driving force is transmitted to the input shaft. The input portion includes a thin shaft portion. The thin shaft portion is provided with a plurality of recesses that extend with the same cross section from at least a position facing the plurality of spherical bodies to a tip on the impact rotary tool side.

The tool system according to one aspect of the present disclosure includes an impact rotary tool attachment and an impact rotary tool to which the impact rotary tool attachment is attached.

According to the present disclosure, it is possible to provide an attachment for an impact rotary tool and a tool system that can be easily removed from the impact rotary tool.

FIG. 1 is an exploded perspective view of a tool system according to a first embodiment. FIG. 2 is a perspective view of the same tool system as above. FIG. 3 is a cross-sectional view of a main part of the rotary impact tool. FIG. 4 is a cross-sectional view of the main parts of the tool system. FIG. 5 is a perspective view of a main part of the driving force conversion mechanism of the attachment for a rotary impact tool according to the first embodiment. FIG. 6 is a front view of the connecting shaft of the impact rotary tool attachment same as above. FIG. 7 is a front view of a connecting shaft of an attachment for an impact rotary tool according to a modification. FIG. 8 is an exploded perspective view of the tool system according to the second embodiment. FIG. 9 is a cross-sectional view of a main part of the tool system. FIG. 10 is a side view of a main part of the driving force conversion mechanism of the impact rotary tool attachment according to the second embodiment. FIG. 11A is a schematic diagram showing one aspect of the tool system according to the third embodiment. FIG. 11B is a schematic diagram showing another aspect of the tool system according to the third embodiment. FIG. 12 is a schematic diagram of a tool system according to a modification of the third embodiment.

Hereinafter, preferred embodiments of the present disclosure will be described in detail with reference to the drawings. In each of the embodiments described below, common elements are given the same reference numerals, and redundant explanations of the common elements will be omitted. Each embodiment below is only one of various embodiments of the present disclosure. Each embodiment can be modified in various ways depending on the design, etc., as long as the objective of the present disclosure can be achieved. Each figure described in this disclosure is a schematic diagram, and the respective ratios of the sizes and thicknesses of each component in each figure do not necessarily reflect the actual dimensional ratios. Note that the arrows indicating each direction in the drawings are merely examples, and are not intended to define the directions when the tool system 100 is used. Further, arrows indicating each direction in the drawings are merely shown for explanation and have no substance.

(Embodiment 1)
(1) Overview First, an overview of the tool system 100 according to the present embodiment will be described with reference to FIGS. 1 to 4.

As shown in FIG. 1, the tool system 100 of this embodiment includes an impact rotary tool 1 and an impact rotary tool attachment 7 (hereinafter referred to as "attachment 7"). As shown in FIG. 2, the attachment 7 is attached to the impact rotary tool 1 and used integrally with the impact rotary tool 1.

The impact rotary tool 1 of this embodiment operates using power (electric power, etc.) from a power source such as a battery pack 25, for example. Specifically, as shown in FIG. 3, the electric motor 3 supplied with power from the battery pack 25 (see FIG. 1) rotates, and rotational driving force is transmitted to the first output shaft 450. When a tip tool such as a driver bit is attached to the first output shaft 450, the impact rotary tool 1 can attach a fastening component such as a screw to be worked on.

As shown in FIG. 3, the impact rotary tool 1 of this embodiment includes two (pair) steel balls 65 (spherical bodies) to prevent the tip tool attached to the first output shaft 450 from coming off. We are prepared. When the tip tool is inserted into the insertion opening 62, the two steel balls 65 sandwich the tip tool in the vertical direction by the elastic force of the spring 66. By sandwiching the tip tool between the two steel balls 65, the tip tool attached to the first output shaft 450 can be made difficult to come off.

The attachment 7 is attached to the impact rotary tool 1, as shown in FIG. As shown in FIG. 4, the attachment 7 includes a connecting shaft 72 to which the rotational driving force is transmitted from the first output shaft 450 of the impact rotary tool 1, and a connecting shaft 72 to which the rotational driving force is transmitted from the impact rotary tool 1 via the connecting shaft 72. and an input shaft 71. The connecting shaft 72 of this embodiment has an input part 721 and an output part 722. The input portion 721 is a portion to which rotational driving force is transmitted from the impact rotary tool 1 in the axial direction (front-rear direction) of the connecting shaft 72 . The output portion 722 is a portion that extends forward from the input portion 721 along the front-rear direction and transmits rotational driving force to the input shaft 71.

The input portion 721 of this embodiment includes a thin shaft portion 723 having a thinner portion than the output portion 722 from a position facing at least two steel balls 65 to a tip on the impact rotary tool 1 side. Since the thin shaft portion 723 has a thinner portion than the output portion 722, the pressing caused by the two steel balls 65 can be reduced. Therefore, the attachment 7 of this embodiment can be easily removed from the impact rotary tool 1. Further, the possibility that the input portion 721 is depressed by being pressed against the two steel balls 65 can be reduced.

(2) Details Hereinafter, a detailed configuration of the tool system 100 according to this embodiment will be described with reference to FIGS. 1 to 6. FIG.

As shown in FIG. 1, a tool system 100 according to the present embodiment includes an impact rotary tool 1 and an attachment 7. Further, as shown in FIG. 2, the attachment 7 is fixed to the impact rotary tool 1 at the tip end portion 211 (see FIG. 1) of the impact rotary tool 1 by a mounting mechanism 8 (see FIG. 4) provided in the attachment 7. .

(2.1) Configuration of Impact Rotary Tool First, the configuration of the impact rotary tool 1 in the tool system 100 according to the present embodiment will be described with reference to FIGS. 1 to 3. In the following description, the direction in which a drive shaft 41 (see FIG. 3) and the first output shaft 450 are lined up is defined as the front-rear direction, and the first output shaft 450 side when viewed from the drive shaft 41 is defined as the front. When viewed from the first output shaft 450, the drive shaft 41 side is the rear. In addition, in the following description, the direction in which the body part 21 and the grip part 22, which will be described later, are lined up is defined as the vertical direction. Place part 22 at the bottom.

As shown in Figs. 1 and 2, the impact rotary tool 1 of this embodiment is used in a tool system 100. A rechargeable battery pack 25 is detachably attached to the impact rotary tool 1. The impact rotary tool 1 of this embodiment operates using the battery pack 25 as a power source. That is, the battery pack 25 is a power source that supplies a current to drive the electric motor 3 (see Fig. 3). The battery pack 25 is not a component of the impact rotary tool 1. However, the impact rotary tool 1 may be equipped with the battery pack 25. The battery pack 25 includes a battery pack configured by connecting multiple secondary batteries (e.g., lithium ion batteries) in series, and a case that houses the battery pack.

As shown in FIG. 3, the impact rotating tool 1 includes a body 2, an electric motor 3, a transmission mechanism 4, and a trigger volume 24.

The body 2 houses an electric motor 3 and a part of the transmission mechanism 4, as shown in FIG. As shown in FIG. 2, the body 2 includes a trunk section 21, a grip section 22, and a mounting section 23. The body portion 21 has a cylindrical shape with an open end (front end) and a bottomed rear end. The grip portion 22 projects downward from the body portion 21. The mounting portion 23 is configured such that a battery pack 25 is removably mounted thereon. In this embodiment, the mounting portion 23 is provided at the tip (lower end) of the grip portion 22. In other words, the body part 21 and the mounting part 23 are connected by the grip part 22.

The trigger volume 24 protrudes from the grip portion 22. The trigger volume 24 is an operation unit that receives operations for controlling the rotation of the electric motor 3 (see FIG. 3). The electric motor 3 can be switched on and off by pulling the trigger volume 24. The rotation speed of the electric motor 3 can be adjusted by the pulling amount of the trigger volume 24. The greater the pulling amount, the faster the rotation speed of the electric motor 3.

The electric motor 3 shown in FIG. 3 is, for example, a brushless motor. The electric motor 3 includes a rotating shaft 31 and converts electric power supplied from the battery pack 25 (see FIG. 2) into rotational driving force for the rotating shaft 31.

The transmission mechanism 4 shown in FIG. 3 is located in front of the electric motor 3 in the internal space of the body section 21. The transmission mechanism 4 includes an impact mechanism 40 and a planetary gear mechanism 48. The impact mechanism 40 includes a drive shaft 41, a hammer 42, a return spring 43, an anvil 45, and two steel balls 49 (rolling elements). The rotational driving force of the rotating shaft 31 of the electric motor 3 is transmitted to the drive shaft 41 via the planetary gear mechanism 48 . The drive shaft 41 is arranged between the electric motor 3 and the first output shaft 450.

The hammer 42 moves relative to the anvil 45, receives power from the electric motor 3, and applies a rotational blow to the anvil 45. The hammer 42 includes a hammer body 420 and two (one in FIG. 3) protrusions 425. The two protrusions 425 protrude from the surface of the hammer body 420 on the first output shaft 450 side. The hammer body 420 has a through hole 421 through which the drive shaft 41 is passed. Further, the hammer body 420 has two grooves 423 on the inner peripheral surface of the through hole 421. The drive shaft 41 has two grooves 413 on its outer peripheral surface. The two groove portions 413 are connected. Two steel balls 49 are sandwiched between the two grooves 423 and the two grooves 413. The two grooves 423, the two grooves 413, and the two steel balls 49 constitute a cam mechanism. While the two steel balls 49 are moving, the hammer 42 is movable in the axial direction of the drive shaft 41 and rotatable with respect to the drive shaft 41. As the hammer 42 moves toward or away from the anvil 45 along the axial direction of the drive shaft 41, the hammer 42 rotates with respect to the drive shaft 41.

The anvil 45 includes a first output shaft 450, two striking parts 451, and a base 452. The base 452 has a disk shape when viewed from the front and rear directions, and its center generally coincides with the central axis of the drive shaft 41. The first output shaft 450 holds a tip tool or connection shaft 72 (see FIG. 4). The first output shaft 450 has a cylindrical shape and protrudes forward from the base 452. The two striking parts 451 protrude from the base 452 in the radial direction of the base 452. The anvil 45 faces the hammer body 420 in the axial direction of the drive shaft 41. Further, when the impact mechanism 40 is not performing a striking operation, the two protrusions 425 of the hammer 42 and the two striking parts 451 of the anvil 45 are in contact with each other in the rotational direction of the drive shaft 41, while the hammer 42 and the anvil 45 are in contact with each other. rotates as one. Therefore, at this time, the drive shaft 41, the hammer 42, and the anvil 45 (first output shaft 450) rotate together.

The return spring 43 is sandwiched between the hammer 42 and the planetary gear mechanism 48. The return spring 43 of this embodiment is a conical coil spring. The impact mechanism 40 further includes a plurality of (two in FIG. 3) steel balls 50 and a ring 51 sandwiched between the hammer 42 and the return spring 43. Thereby, the hammer 42 is rotatable relative to the return spring 43. The hammer 42 receives a force directed toward the first output shaft 450 from the return spring 43 in the axial direction of the drive shaft 41 .

Hereinafter, the movement of the hammer 42 toward the anvil 45 in the axial direction of the drive shaft 41 will be referred to as "the hammer 42 moving forward." Furthermore, hereinafter, the movement of the hammer 42 in a direction away from the anvil 45 in the axial direction of the drive shaft 41 will be referred to as "the hammer 42 moving backward."

In the impact mechanism 40, a striking operation is started when the load torque exceeds a predetermined value. That is, as the load torque increases, the component of the force generated between the hammer 42 and the anvil 45 in the direction of retracting the hammer 42 also increases. When the load torque exceeds a predetermined value, the hammer 42 moves backward while compressing the return spring 43. Then, as the hammer 42 moves backward, the two protrusions 425 of the hammer 42 get over the two striking parts 451 of the anvil 45, and the hammer 42 rotates. Thereafter, the hammer 42 receives the return force from the return spring 43 and moves forward. Then, when the drive shaft 41 rotates approximately half a rotation, the two protrusions 425 of the hammer 42 collide with the sides of the two striking parts 451 of the anvil 45. In the impact mechanism 40, the two protrusions 425 of the hammer 42 collide with the two striking parts 451 of the anvil 45 every time the drive shaft 41 rotates approximately half a rotation. That is, the hammer 42 applies a rotational impact to the anvil 45 every time the drive shaft 41 rotates approximately half a rotation.

In this way, in the impact mechanism 40, collisions between the hammer 42 and the anvil 45 repeatedly occur. Due to the torque generated by this collision, fastening members such as screws, bolts, or nuts can be tightened more strongly than in the case where there is no collision.

Such a transmission mechanism 4 is housed in a metal hammer case 400. The hammer case 400 has a circular through hole 402 on its front surface 401, through which the first output shaft 450 passes. The hammer case 400 also has a protrusion 403 that protrudes forward from the peripheral edge of the through hole 402 . The protrusion 403 has a cylindrical shape. The protrusion 403 has a plurality of (two in the example of FIG. 3) recesses 404 provided on the outer peripheral surface. The claw portion 81 of the attachment 7 is caught in the recess 404 (see FIG. 4).

The first output shaft 450 has an insertion port 62 and a fixing mechanism 63. A tip tool such as a driver bit or a connecting shaft 72 (rod-shaped body) of the attachment 7 is attached to the insertion opening 62 . The shape of the insertion port 62 in this embodiment is a regular hexagon when viewed from the axial direction (front-back direction) of the connecting shaft 72. The term "regular hexagonal shape" as used in the present disclosure is not limited to a "regular hexagon" in which six sides are equal in length and six interior angles are equal; Also includes "shape".

For example, when a driver bit is attached to the first output shaft 450, the transmission mechanism 4 transmits the rotational driving force of the rotating shaft 31 of the electric motor 3 to the driver bit via the first output shaft 450. This causes the driver bit to rotate. By rotating the driver bit while the driver bit is in contact with a fastening member (such as a screw), it is possible to tighten or loosen the fastening member. The transmission mechanism 4 includes an impact mechanism 40. The impact rotary tool 1 of this embodiment is an electric impact driver that can tighten screws while performing a striking action using the impact mechanism 40. In the impact operation, impact force is applied to a fastening member such as a screw via the first output shaft 450.

Further, when the connecting shaft 72 of the attachment 7 is attached to the first output shaft 450 (see FIG. 4), the transmission mechanism 4 transfers the rotational driving force of the rotating shaft 31 of the electric motor 3 to the first output shaft 450. The signal is transmitted to the connecting shaft 72 via the connecting shaft 72. This causes the connecting shaft 72 to rotate. As the connection shaft 72 rotates, the connection shaft 72 transmits rotational driving force to the input shaft 71 of the attachment 7 . The operation of the attachment 7 after the rotational driving force is transmitted to the input shaft 71 will be described later in "(2.2) Configuration of Attachment".

The fixing mechanism 63 has a plurality of holes 64 (two in the example of FIG. 3), a plurality of steel balls 65 (spherical bodies), a spring 66, a bit holder 67, and a spring 68. The fixing mechanism 63 is a mechanism for holding a tip tool such as a driver bit with respect to the impact rotary tool 1. The two holes 64 are provided at the upper and lower ends of the insertion port 62 forward of the tip of the protruding portion 403 of the hammer case 400, and are elliptical holes with the longitudinal direction being the front-rear direction. The two steel balls 65 are fitted into the two holes 64. The bit holder 67 has a cylindrical shape with openings on the front and rear sides, and covers the outer periphery of the first output shaft 450 at the tip side of the first output shaft 450. The spring 66 is a spiral-shaped spring that covers the outer periphery of the first output shaft 450 between the first output shaft 450 and the bit holder 67. When the tool tip is inserted into the insertion opening 62, the tool tip pushes the two steel balls 65 in a vertically and obliquely backward direction against the elastic force of the spring 66. When the tool tip is inserted into the insertion opening 62, the two steel balls 65 sandwich the tool tip in the vertical direction by the elastic force of the spring 66. When the tool tip is provided with a groove corresponding to the steel balls 65, the groove of the tool tip and the steel balls 65 are fitted together, thereby fixing the tool tip to the impact rotary tool 1. The spring 68 is a spiral spring located forward of the spring 66 and covers the outer periphery of the first output shaft 450 between the first output shaft 450 and the bit holder 67. By moving the bit holder 67 forward against the elastic force of the spring 68, a space is created between the bit holder 67 and the spring 66 in the vertical direction of the two holes 64. When the two steel balls 65 move into this space, the grooves of the tool tip and the steel balls 65 are released from their engagement.

As described above, the two (pair) steel balls 65 are movable in the front-back direction and the up-down direction. When the tip tool is not pushing the two steel balls 65 diagonally backward in the vertical direction against the elastic force of the spring 66 (default state), the distance between the two steel balls 65 in the vertical direction is the minimum distance W1. becomes. Furthermore, the connecting shaft 72 of the attachment 7 of this embodiment does not have a groove portion into which the steel ball 65 fits.

In this way, the first output shaft 450 is configured to hold a tip tool such as a driver bit. Note that in this embodiment, the tip tool is not included in the configuration of the impact rotary tool 1.

(2.2) Configuration of Attachment Next, the configuration of the attachment 7 in the tool system 100 according to the present embodiment will be described with reference to FIGS. 4 to 6.

As shown in FIG. 4, the attachment 7 according to the present embodiment includes a housing 70, an input shaft 71, a connecting shaft 72, a second output shaft 73, an attachment mechanism 8, and a driving force conversion mechanism 9. We are prepared.

The housing 70 accommodates an input shaft 71 , a connection shaft 72 , a part of the second output shaft 73 , a part of the attachment mechanism 8 , and the driving force conversion mechanism 9 .

The connecting shaft 72 connects the first output shaft 450 and the input shaft 71 and drives the first output shaft 450 and the input shaft 71 integrally. The connecting shaft 72 transmits the rotational driving force of the first output shaft 450 from the first output shaft 450 to the input shaft 71.

Further, the connecting shaft 72 has an input portion 721 and an output portion 722.

The input portion 721 is a portion to which rotational driving force is transmitted from the impact rotary tool 1 in the axial direction (front-rear direction) of the connecting shaft 72 . Moreover, the input part 721 is a part inserted into the insertion opening 62 of the impact rotary tool 1. The input portion 721 has a regular hexagonal column shape as a whole, and has a shape corresponding to the shape of the insertion opening 62 of the impact rotary tool 1. Specifically, the cross-sectional shape of input portion 721 and the shape of insertion port 62 are the same shape. For example, when the insertion port 62 has a regular hexagonal shape as in this embodiment, the cross-sectional shape of the input portion 721 has a regular hexagonal shape. The shape of the insertion port 62 is a regular hexagon. A "regular hexagonal columnar shape" as used in the present disclosure means that the bottom surface and the top surface are "regular hexagonal", the six sides connecting the corresponding vertices of the bottom surface and the top surface are equal in length, and the six sides and the bottom surface and the top surface are the same length. It is not limited to orthogonal "regular hexagonal prisms," but also includes "shapes that can be considered as regular hexagonal prisms" similar to the regular hexagonal prisms.

Input portion 721 includes a thin shaft portion 723 . The thin shaft portion 723 has a thinner portion than the output portion 722 from the position facing at least two steel balls 65 to the tip on the impact rotary tool 1 side. As shown in FIG. 4, since the thin shaft portion 723 has a thinner portion than the output portion 722 in the direction facing the two steel balls 65, the attachment 7 of this embodiment can be inserted into and removed from the impact rotary tool 1. It's easy to do.

The thin shaft portion 723 of this embodiment is thinner than the output portion 722 because a plurality of recesses 724 (see FIG. 5) are provided from the position facing the two steel balls 65 to the tip of the impact rotary tool 1. In the examples of FIGS. 4 and 6, the width W2 between the two (pair) recesses 724 of the thin shaft portion 723 in the direction (vertical direction) orthogonal to the axial direction (front-back direction) of the connecting shaft 72 is 722 width W3. On the other hand, the portion of the input portion 721 of this embodiment that is not the thin shaft portion 723 has the same shape and size as the output portion 722. That is, the width of the portion of the input portion 721 that is not the thin shaft portion 723 in the vertical direction is equal to the width W3 of the output portion 722.

Furthermore, the width W2 between the pair of recesses 724 in this embodiment is equal to or less than the minimum distance W1 (see FIG. 3) between the pair of steel balls 65. In other words, in the vertical direction, the width W2 of the portion of the thin shaft portion 723 that faces the pair of steel balls 65 is equal to or less than the minimum distance W1 between the pair of steel balls 65. The width W2 can also be said to be the width of the thin shaft portion 723 in the direction that faces the steel ball 65. Because the width W2 between the pair of recesses 724 is equal to or less than the minimum distance W1 between the pair of steel balls 65, the thin shaft portion 723 in this embodiment can reduce the force pressing from the steel ball 65.

As shown in FIG. 6, the thin shaft portion 723 has a recess 724 on each side of a regular hexagonal column. That is, six recesses 724 are provided in the thin shaft portion 723 of this embodiment.

As shown in FIG. 6, each of the six recesses 724 has an arc shape when viewed in plan from the axial direction of the connecting shaft 72, and has a shape along the steel ball 65.

The thin shaft portion 723 also has six protrusions 725 between adjacent recesses 724 in the six recesses 724. Here, in this embodiment, each of the six protrusions 725 is a part of each vertex of a regular hexagon. When the input part 721 is inserted into the insertion port 62 of the impact rotary tool 1, each of the six protrusions 725 comes into contact with the inner wall 621 of the insertion port 62. Because the protrusions 725 come into contact with the inner wall 621 of the insertion port 62, the rotational driving force from the impact rotary tool 1 is also transmitted to the thin shaft portion 723.

As shown in FIG. 4, the output portion 722 is a portion that extends forward from the input portion 721 along the front-rear direction and transmits rotational driving force to the input shaft 71. The shape of the output portion 722 in this embodiment is a regular hexagonal column, and corresponds to the shape of the insertion opening 711 of the input shaft 71. Specifically, the cross-sectional shape of the output portion 722 and the shape of the insertion port 711 are the same shape. For example, when the output portion 722 has a regular hexagonal column shape as in this embodiment, the cross-sectional shape of the output portion 722 is a regular hexagon, so the shape of the insertion port 711 is a regular hexagon. The output portion 722 of this embodiment is press-fitted into the insertion port 711 of the input shaft 71. In other words, the connecting shaft 72 and the input shaft 71 of this embodiment are integrally configured, and the connecting shaft 72 and the input shaft 71 are driven integrally.

The attachment mechanism 8 fixes the housing 70 of the attachment 7 to the tip portion 211 of the impact rotary tool 1. The attachment mechanism 8 includes a plurality of (two in FIG. 4) claw portions 81 and a plurality of (two in FIG. 4) springs 82.

The claw portion 81 has a surface portion 811 , a base portion 812 , a shaft portion 813 , a protrusion portion 814 , and a hook portion 816 . The surface portion 811 is exposed from the housing 70 and has a rectangular shape when viewed from above and below. The base portion 812 protrudes toward the connecting shaft 72 on the rear side of the surface portion 811 . The shaft portion 813 is a shaft provided at a tip 815 of the base portion 812 on the side of the connecting shaft 72 and extends in the left-right direction. The shaft portion 813 is rotatably supported by a bearing 707 included in the inner wall 701 of the housing 70 . The protruding portion 814 protrudes from the back side (inside) of the surface portion 811 toward the connecting shaft 72 and has a cylindrical shape. A spiral spring 82 is wound around the outer periphery of the protrusion 814 . The spring 82 is disposed between the surface portion 811 and the inner wall 701, with the protrusion portion 814 housed in the inner peripheral portion. The hook portion 816 protrudes rearward from the connecting shaft 72 side of the rear end of the base portion 812, and has a hook shape. When the tip 818 (lower end or upper end) of the hook portion 816 is caught in the recess 404 of the hammer case 400, the claw portion 81 fixes the housing 70 of the attachment 7 to the impact rotary tool 1. The claw portion 81 presses the recess 404 of the hammer case 400 toward the connecting shaft 72 by the elastic force of the spring 82 .

Further, the claw portion 81 further includes an operation portion 817. When the user of the impact rotary tool 1 applies force to the operating portion 817 in a direction opposite to the elastic force of the spring 82, that is, toward the connecting shaft 72 side, the hook portion 816 moves outward (the connecting shaft 72 (in the direction away from). In other words, when the user applies force to the operating portion 817 in a direction opposite to the elastic force of the spring 82, the engagement between the tip 818 of the hook portion 816 and the recess 404 is released. That is, the claw portion 81 is displaced by the elastic force of the spring 82 between the position where it is caught in the recess 404 and the position where it is released from the recess 404 .

The input shaft 71 is arranged on the front side of the connecting shaft 72 so that the central axis of the input shaft 71 generally coincides with the central axis of the connecting shaft 72. As described above, the input shaft 71 is driven integrally with the connecting shaft 72, and rotational driving force is transmitted from the connecting shaft 72. The input shaft 71 is rotatably supported by bearings 702 fixed to two inner walls 701 of the housing 70 .

The driving force conversion mechanism 9 includes a first gear 91 provided on the outer periphery of the input shaft 71 and a second gear 92 provided on the outer periphery of the second output shaft 73. The first gear 91 and the input shaft 71 are driven integrally. Further, the second gear 92 and the second output shaft 73 are driven integrally. Further, as shown in FIG. 5, the driving force conversion mechanism 9 further includes a third gear 93 located between the first gear 91 and the second gear 92 in the vertical direction. The third gear 93 has a shaft 931 parallel to the input shaft 71 and the second output shaft 73. Each of the first gear 91, the second gear 92, and the third gear 93 is a spur gear having a plurality of teeth protruding in the radial direction. The first gear 91 and the third gear 93 are in mesh with each other, and the third gear 93 and the second gear 92 are in mesh with each other.

Further, the driving force conversion mechanism 9 further includes a pair of support plates 94. The pair of support plates 94 are located in front of the tip (front end) of the connecting shaft 72. The pair of support plates 94 are positioned at intervals greater than the axial lengths of the first gear 91, the second gear 92, and the third gear 93 in the front-rear direction. The pair of support plates 94 rotatably support the input shaft 71, the shaft 931 of the third gear 93, and the second output shaft 73.

When the rotational driving force is transmitted to the input shaft 71, the input shaft 71 and the first gear 91 rotate integrally. Since the first gear 91 and the third gear 93 mesh with each other, when the first gear 91 rotates, rotational driving force is transmitted from the first gear 91 to the third gear 93. The third gear 93 to which the rotational driving force is transmitted from the first gear 91 rotates in a direction opposite to the rotation direction of the first gear 91. Since the third gear 93 and the second gear 92 mesh with each other, when the third gear 93 rotates, rotational driving force is transmitted from the third gear 93 to the second gear 92. The second gear 92 to which the rotational driving force is transmitted from the third gear 93 rotates in a direction opposite to the rotation direction of the third gear 93. That is, the second gear 92 rotates in the same direction as the first gear 91. The third gear 93 is driven integrally with the second output shaft 73, and the rotational driving force transmitted to the third gear 93 is transmitted to the second output shaft 73.

As described above, the driving force conversion mechanism 9 of this embodiment indirectly transmits rotational driving force from the first gear 91 to the second gear 92 via the third gear 93. The rotation axis Ax1 of the input shaft 71 and the rotation axis Ax2 of the second output shaft 73 are generally parallel. That is, the driving force conversion mechanism 9 of this embodiment, when transmitting the rotational driving force from the input shaft 71 to the second output shaft 73, performs parallel movement of the rotation axis Ax0 of rotation by the rotational driving force. Specifically, the driving force conversion mechanism 9 of this embodiment moves the rotational axis Ax0 of rotation by the rotational driving force from the rotational axis Ax1 of the input shaft 71 to the rotational axis Ax2 of the second output shaft 73.

The second output shaft 73 is rotatably supported by a bearing 703 fixed to the housing 70, as shown in FIG. The second output shaft 73 is generally parallel to the input shaft 71 and is aligned with the input shaft 71 in the vertical and horizontal directions. The second output shaft 73 has an insertion port 731 and a fixing mechanism 732. A tip tool such as a driver bit is attached to the insertion opening 731. When a driver bit is attached to the second output shaft 73, when the second output shaft 73 rotates, the driver bit rotates integrally with the second output shaft 73. By rotating the driver bit while the driver bit is in contact with a fastening member (such as a screw), it is possible to tighten or loosen the fastening member.

The fixing mechanism 732 includes a plurality of holes 733 (two in the example of FIG. 4), a plurality of steel balls 734 (two in the example of FIG. 3), a spring 735, a bit holder 736, and a spring 737. are doing. The two holes 733 are provided at the upper and lower ends of the insertion port 731 on the front side of the tip of the housing 70, and are oval-shaped holes whose longitudinal direction is the front-rear direction. Two steel balls 734 are fitted into two holes 733. The bit holder 736 has a cylindrical shape with open front and rear surfaces, and covers the outer periphery of the second output shaft 73 in front of the tip of the housing 70 . The spring 735 is a helical spring that covers the outer periphery of the second output shaft 73 between the second output shaft 73 and the bit holder 736. When the tip tool is inserted into the insertion port 731, the tip tool pushes the two steel balls 734 upward and downward diagonally rearward against the elastic force of the spring 735. When the tip tool is inserted into the insertion port 731, the two steel balls 734 sandwich the tip tool in the vertical direction by the elastic force of the spring 735. When the tip tool is provided with a groove corresponding to the steel ball 734, the tip tool is fixed to the attachment 7 by fitting the groove of the tip tool and the steel ball 734. The spring 737 is a helical spring that is located in front of the spring 735 and covers the outer periphery of the second output shaft 73 between the second output shaft 73 and the bit holder 736. By moving the bit holder 736 forward against the elastic force of the spring 737, a space is created between the bit holder 736 and the spring 735 in the vertical direction of the two holes 733. By moving the two steel balls 734 into this space, the fitting between the groove of the tip tool and the steel balls 734 is released.

The load torque of the second output shaft 73 is transmitted to the first output shaft 450 via the second gear 92 , the third gear 93 , the first gear 91 , the input shaft 71 , and the connection shaft 72 . As described above, the impact mechanism 40 applies an impact force in the rotational direction to the first output shaft 450 when the load torque of the first output shaft 450 exceeds a predetermined level. This impact force in the rotational direction is transmitted to the second output shaft 73 via the connecting shaft 72, the input shaft 71, the first gear 91, the third gear 93, and the second gear 92, similarly to the rotational driving force. Thereby, the second output shaft 73 (attachment 7) can apply a larger tightening torque to a work object such as a tightening part.

(3) Effects As described above, the tool system 100 of this embodiment includes the impact rotary tool 1 and the attachment 7. The attachment 7 includes a connection shaft 72 and an input shaft 71. The connecting shaft 72 is inserted into the insertion port 62 and faces each of the two steel balls 65 of the impact rotary tool 1, and the rotational driving force from the impact rotary tool 1 is transmitted thereto. Further, the connecting shaft 72 has an input portion 721 and an output portion 722. The input portion 721 has a thinner portion than the output portion 722 from the position facing at least two steel balls 65 to the tip on the impact rotary tool 1 side. Since the thin shaft portion 723 extends from the position facing the two steel balls 65 to the tip on the impact rotary tool 1 side, the pressing force from the two steel balls 65 can be reduced, and the input portion 721 (connection This makes it easier to pull out the shaft 72). Therefore, the attachment 7 of this embodiment can be easily removed from the impact rotary tool 1.

Further, the thin shaft portion 723 of this embodiment is thinner than the output portion 722 because six recesses 724 are provided from the position facing the two steel balls 65 to the tip on the impact rotary tool 1 side. Therefore, by processing a connecting shaft that does not have a thin shaft portion 723 to provide a recess 724, the connecting shaft 72 having a thin shaft portion 723 can be easily manufactured.

Further, the six recesses 724 of this embodiment are arcuate in plan view from the axial direction of the connecting shaft 72. Thereby, the recessed portion 724 can be formed into a shape along the steel ball 65. Therefore, even if the recessed portion 724 and the steel ball 65 come into contact, the contact area becomes large, so that the portion in contact with the steel ball 65 is unlikely to be depressed.

Further, the thin shaft portion 723 of this embodiment has six convex portions 725 between the six concave portions 724 adjacent to each other. Each of the six protrusions 725 contacts the inner wall 621 of the insertion port 62. Since each of the six convex portions 725 comes into contact with the inner wall 621 of the insertion port 62, rotational driving force is transmitted from the impact rotary tool 1 to the thin shaft portion 723 via the six convex portions 725.

Furthermore, the attachment 7 of the present embodiment includes a housing 70 that accommodates at least a portion of the connecting shaft 72 and the input shaft 71, and a mounting mechanism that attaches and fixes the housing 70 to the tip portion 211 of the impact rotary tool 1. 8. By providing the attachment mechanism 8 with the attachment mechanism 8, the attachment 7 can be fixed to the impact rotary tool 1. Further, since the housing 70 is fixed to the tip portion 211 of the impact rotary tool 1 relatively close to the attachment 7, vibration of the attachment 7 relative to the impact rotary tool 1 can be reduced.

Further, the width W2 in the vertical direction of the portion of the thin shaft portion 723 of this embodiment that faces the two (pair) steel balls 65 (spherical bodies) is equal to or less than the minimum distance W1 in the vertical direction between the two steel balls 65. It is. Since the pressing of the two steel balls 65 against the thin shaft portion 723 can be almost reduced, the attachment 7 can be easily attached to and detached from the impact rotary tool 1.

Further, the output portion 722 of the connecting shaft 72 of this embodiment is press-fitted into the input shaft 71. Since the connecting shaft 72 and the input shaft 71 are integrated, it is possible to reduce the possibility that the connecting shaft 72 will fall or be lost when the attachment 7 is attached to and removed from the impact rotary tool 1.

(4) Modifications Below, we will list modifications of the first embodiment. The modifications described below can be applied in appropriate combination with the first embodiment.

The driving force conversion mechanism 9 not only translates the rotational axis Ax0 of rotation by the rotational driving force, but also changes the angle of the rotational axis Ax0 and converts the rotational driving force into a thrust driving force along the rotational axis Ax0. It may be configured to perform the following.

The driving force conversion mechanism 9 may have a gear other than the third gear 93 as a path for transmitting the rotational driving force from the first gear 91 to the second gear 92. That is, the driving force conversion mechanism 9 may have four or more gears for transmitting rotational driving force from the input shaft 71 to the second output shaft 73.

It is not essential that the driving force conversion mechanism 9 has the third gear 93, and the rotational driving force may be transmitted directly from the first gear 91 to the second gear 92. In this case, the first gear 91 and the second gear 92 are arranged to mesh with each other. Note that when the rotational driving force is transmitted directly from the first gear 91 to the second gear 92, the rotational direction of the first gear 91 (input shaft 71) and the rotational direction of the second gear 92 (second output shaft 73) are opposite to each other.

It is not essential for the attachment mechanism 8 to have the spring 82; for example, the hook 816 may be pressed against the recess 404 of the hammer case 400 by the elastic force of the hook 816 itself.

The parts other than the hammer case 400, such as a part of the body part 21 of the impact rotary tool 1, may be made of metal so that the attachment mechanism 8 can be attached.

The shape of the insertion port 62 is not limited to a regular hexagonal shape. The shape of the insertion port 62 may be other regular polygonal shapes such as an equilateral triangle or a square. Here, the term "regular polygon" refers to not only a "regular polygon" in the strict sense in which all sides are equal in length and all interior angles are equal, but also a "regular polygon" similar to this regular polygon. It also includes "shapes that can be considered polygons." Moreover, the shape of the insertion port 62 may be circular or elliptical.

The shape of the input portion 721 is not limited to a regular hexagonal column. The shape of the input portion 721 may be a regular triangular prism or another regular polygonal prism such as a square prism. Here, "regular polygonal column" means a "regular polygon" whose bottom and top surfaces are the same, all sides connecting corresponding vertices of the bottom and top surfaces are equal in length, and all sides, bottom and top surfaces are the same. It includes not only "regular polygonal prisms" in the strict sense of orthogonal polygons, but also "shapes that can be considered regular polygonal prisms" that are similar to these regular polygonal prisms. Furthermore, the input portion 721 may have a cylindrical shape or an elliptical cylindrical shape.

It is not an essential configuration that the thin shaft portion 723 of the connecting shaft 72 has the concave portion 724 and the convex portion 725. As shown in FIG. 7, the thin shaft portion 723 of the modified example does not have a recess 724 and a convex portion 725. The thin shaft portion 723 of the modified example has a regular hexagonal shape when viewed from the axial direction of the connecting shaft 72, and has a regular hexagonal column shape extending toward the output portion 722 along the axial direction. Similar to the first embodiment, the width W2 of the thin shaft portion 723 in the vertical direction is smaller than the width W3 of the output portion 722 in the vertical direction.

The shape of the thin shaft portion 723 is not limited to a regular hexagonal prism, but may be another regular polygonal prism, or may be a cylindrical or elliptical cylinder. The width W2 of the thin shaft portion 723 in the direction facing the steel ball 65 must be smaller than the width W3 of the output portion 722 in the same direction.

The shape of the output part 722 is not limited to a regular hexagonal prism. The shape of the output part 722 may be another regular polygonal prism. The shape of the output part 722 may also be a circular cylinder or an elliptical cylinder.

In the first embodiment, the impact rotary tool 1 is an impact driver, for example. However, the impact rotary tool 1 is not limited to an impact driver, and may be an impact wrench, for example.

(Embodiment 2)
(1) Overview As shown in FIG. 8, the tool system 100 of this embodiment includes an attachment 7a that converts the angle of the rotational axis Ax0 of the rotational driving force transmitted to the input shaft 71 (see FIG. 9). This differs from the tool system 100 according to the first embodiment (see FIG. 4) in that the present invention is different from the tool system 100 according to the first embodiment (see FIG. 4). Hereinafter, configurations similar to those in Embodiment 1 will be given the same reference numerals and descriptions will be omitted as appropriate.

(2) Details As shown in FIG. 9, the attachment 7a of this embodiment includes a housing 70, an input shaft 71, a connecting shaft 72, a second output shaft 73, an attachment mechanism 8, and a driving force conversion mechanism 9a.

The input shaft 71 of this embodiment is rotatably supported by a bearing 704 fixed to the housing 70.

The second output shaft 73 of this embodiment is provided at a position intersecting the input shaft 71. Specifically, the input shaft 71 runs along the front-back direction, whereas the second output shaft 73 runs along the up-down direction. The second output shaft 73 is rotatably supported by a bearing 705 and a bearing 706 that are fixed to the housing 70.

The driving force conversion mechanism 9a of this embodiment includes a first gear 91a provided on the outer periphery of the input shaft 71 and a second gear 92a provided on the outer periphery of the second output shaft 73. The first gear 91a and the input shaft 71 are driven integrally. Further, the second gear 92a and the second output shaft 73 are driven integrally.

The first gear 91a and the second gear 92a of this embodiment are bevel gears whose directions are different from each other by 90 degrees, and mesh with each other (see FIG. 10). For example, when the input shaft 71 and the first gear 91a rotate clockwise around the rotation axis Ax1, the second output shaft 73 and the second gear 92a rotate clockwise around the rotation axis Ax3. The rotational axis Ax1 and the rotational axis Ax3 are 90 degrees different in direction and intersect with each other.

As described above, the driving force conversion mechanism 9a of the present embodiment changes the angle of the rotation axis Ax0 of rotation by the rotational driving force when transmitting the rotational driving force from the input shaft 71 to the second output shaft 73. Specifically, the driving force conversion mechanism 9a of the present embodiment changes the angle of the rotational axis Ax0 of rotation by the rotational driving force from the angle of the rotational axis Ax1 of the input shaft 71 to the angle of the rotational axis Ax3 of the second output shaft. do. The angle of the rotation axis Ax0 refers to the angle formed between the axis and the rotation axis Ax0 with respect to a certain axis. Here, the rotation axis Ax1 of the input shaft 71 is used as a reference.

(3) Effect The driving force conversion mechanism 9a of this embodiment includes a first gear 91a provided on the input shaft 71 and a second gear 92a provided on the second output shaft 73. . The driving force conversion mechanism 9a transmits the rotational driving force to the second output shaft 73 intersecting the input shaft 71 by directly transmitting the rotational driving force from the first gear 91a to the second gear 92a. That is, the driving force conversion mechanism 9a of the present embodiment changes the angle of the rotational axis Ax0 of the rotational driving force transmitted to the input shaft 71. As a result, even if the object to be worked on, such as a fastening member, is at an angle where it is difficult to apply force, it is possible to obtain a large tightening torque with a small pressing force, making it easy to perform the work.

(4) Modification Examples Modification examples of the second embodiment will be listed below. The modifications described below can be applied in appropriate combinations with Embodiment 1 and the modifications of Embodiment 1.

The driving force conversion mechanism 9a not only changes the angle of the rotational axis Ax0 of rotation by the rotational driving force, but also moves the rotational axis Ax0 in parallel, and converts the rotational driving force into a thrust driving force along the rotational axis Ax0. It may be configured to perform the following.

In the driving force conversion mechanism 9a, it is not essential that the first gear 91a and the second gear 92a directly mesh with each other; other gears may be arranged between the first gear 91a and the second gear 92a to The rotational driving force may be indirectly transmitted from the second gear 92a to the second gear 92a.

(Embodiment 3)
(1) Overview The tool system 100 of the third embodiment differs from the tool system 100 of the first embodiment in that the attachment 7b is provided as shown in Fig. 11A and Fig. 11B. The attachment 7b of the present embodiment is provided with a driving force conversion mechanism 9b that converts a rotational driving force transmitted to the input shaft 71 into a thrust driving force along the rotation axis Ax0. Hereinafter, the same components as those of the first embodiment will be denoted by the same reference numerals and will not be described as appropriate.

(2) Details As shown in Figures 11A and 11B, the attachment 7b of this embodiment includes a housing 70, an input shaft 71, a connecting shaft 72, a second output shaft 73b, an attachment mechanism 8, a driving force conversion mechanism 9b, a movable blade 74, and a fixed blade 75.

The second output shaft 73b of this embodiment has a longitudinal direction along the rotation axis Ax1 of the input shaft 71. The second output shaft 73b and the input shaft 71 are along the rotation axis Ax0 of rotation due to the rotational driving force. The second output shaft 73b has a cylindrical shape with an opening at the rear end and a bottom at the front end (tip). The second output shaft 73b is disposed on the outer circumferential side of the input shaft 71 so as to cover the input shaft 71 on the inner circumferential side. Further, the second output shaft 73b is supported by the housing 70 so as not to rotate.

The driving force conversion mechanism 9b of this embodiment has a first threaded portion 95 and a second threaded portion 96. The first threaded portion 95 is provided on the outer periphery of the input shaft 71. The second threaded portion 96 is provided on the inner periphery of the second output shaft 73b and is screwed into the first threaded portion 95. When the input shaft 71 rotates, the first screw portion 95 rotates integrally with the input shaft 71. When the first threaded part 95 rotates while the first threaded part 95 and the second threaded part 96 are engaged, a thrust driving force in the longitudinal direction is transmitted to the second threaded part 96. That is, the driving force conversion mechanism 9b of the present embodiment converts the rotational driving force transmitted to the input shaft 71 into a thrust driving force along the rotational axis Ax0 of rotation by the rotational driving force, and converts the thrust driving force into the first thrust driving force. 2 screw portion 96 (second output shaft 73b).

The direction of the longitudinal thrust driving force transmitted to the second threaded portion 96 changes depending on the rotational direction of the first threaded portion 95. For example, when the first threaded portion 95 rotates clockwise around the rotation axis Ax0, forward thrust driving force is transmitted to the second threaded portion 96. When forward thrust driving force is transmitted to the second threaded portion 96, the second output shaft 73 moves forward within the movable range. Further, when the first screw portion 95 rotates counterclockwise around the rotation axis Ax0, a rearward thrust driving force is transmitted to the second screw portion 96. When the rearward thrust driving force is transmitted to the second threaded portion 96, the second output shaft 73b moves rearward within the movable range.

As described above, the driving force conversion mechanism 9b of the present embodiment converts the rotational driving force into the thrust driving force along the rotation axis Ax0 when transmitting the rotational driving force from the input shaft 71 to the second output shaft 73. conduct.

The movable blade 74 is a blade that moves integrally with the second output shaft 73b. If the second output shaft 73b moves forward, the movable blade 74 also moves forward. If the second output shaft 73b moves backward, the movable blade 74 also moves backward. The fixed blade 75 is a blade fixed to the housing 70. As shown in FIG. 11A, the position of the movable blade 74 where the object to be cut T1 can be placed between the movable blade 74 and the fixed blade 75 is referred to as a first position. Further, as shown in FIG. 11B, the position of the movable blade 74 where the movable blade 74 and the fixed blade 75 overlap in the direction perpendicular to the rotation axis Ax1 of the input shaft 71 is referred to as a second position. While the rotational driving force is transmitted to the input shaft 71 and the movable blade 74 is displaced from the first position to the second position, the cutting target T1 is cut by the movable blade 74 and the fixed blade 75.

(3) Effects The driving force conversion mechanism 9b of this embodiment includes a first screw portion 95 provided on the input shaft 71 and a second screw portion 95 provided on the second output shaft 73, which is screwed into the first screw portion 95. 2 screw portions 96. When the driving force conversion mechanism 9b transmits the rotational driving force from the input shaft 71 to the second output shaft 73, the rotation of the first threaded part 95 due to the rotational driving force transmitted to the input shaft 71 converts the second threaded part. 96 and the second output shaft 73b are moved along the rotational axis Ax0 of rotation by the rotational driving force. That is, the driving force conversion mechanism 9b of this embodiment converts the rotational driving force into the thrust driving force by moving the second screw part 96 and the second output shaft 73b along the rotation axis Ax0 by the rotation of the first screw part 95. Perform the conversion to The attachment 7b of this embodiment converts the rotational driving force transmitted to the input shaft 71 into a thrust driving force along the rotational axis Ax0 of the rotational driving force, so that the work that the tool system 100 can handle can be increased. can.

Furthermore, in the tool system 100 of this embodiment, the load torque of the input shaft 71 is transmitted to the first output shaft 450 via the connection shaft 72. As described above, the impact mechanism 40 applies an impact force in the rotational direction to the first output shaft 450 when the load torque of the first output shaft 450 exceeds a predetermined level. Similar to the rotational driving force, this rotational impact force is transmitted to the input shaft 71 via the connecting shaft 72, converted into a thrust driving force by the driving force conversion mechanism 9b, and transmitted to the second output shaft 73b. . Thereby, even if a large force is required to cut the object T1, the object T1 can be easily cut using the thrust driving force converted from the impact force generated by the impact mechanism 40.

(4) Modifications Below, modifications of embodiment 3 are listed. The modifications described below can be applied in appropriate combination with embodiment 1 and the modifications of embodiment 1, and embodiment 2 and the modifications of embodiment 2.

As shown in FIG. 12, the attachment 7c may be an attachment in which the movable blade 74 of the third embodiment is replaced with a movable part 76, and the fixed blade 75 of the third embodiment is replaced with a fixed part 77. The attachment 7c is, for example, a crimping attachment that clamps a pair of objects between the movable part 76 and the fixed part 77 and adheres the pair of objects to each other by applying pressure.

The attachment 7c functions as a crimping attachment by converting the rotational drive force transmitted to the input shaft 71 into a thrust drive force along the rotation axis Ax0 of the rotational drive force. Further, even if a large force is required to press a pair of objects together, the thrust driving force converted from the impact force generated by the impact mechanism 40 can easily press the objects together.

The driving force conversion mechanism 9b not only converts the rotational driving force into a thrust driving force along the rotational axis Ax0 of rotation by the rotational driving force, but also converts the rotational driving force into a thrust driving force along the rotational axis Ax0, and also changes the angle of the rotational axis Ax0. It may be configured to make changes.

(summary)
As explained above, the attachment (7; 7a; 7b; 7c) according to the first aspect includes the connection shaft (72) and the input shaft (71). The connecting shaft (72) is inserted into the insertion port (62) of the impact rotary tool (1), faces each of the plurality of spherical bodies (steel balls 65) of the impact rotary tool (1), and is inserted into the impact rotary tool (1). The rotational driving force from 1) is transmitted. Rotational driving force is transmitted to the input shaft (71) from the impact rotary tool (1) via the connection shaft (72). The connecting shaft (72) has an input part (721) and an output part (722). The input portion (721) is a portion to which rotational driving force is transmitted from the impact rotary tool (1) in the axial direction of the connecting shaft (72). The output portion (722) extends along the axial direction from the input portion (721), and is a portion that transmits rotational driving force to the input shaft (71). The input portion (721) includes a thin shaft portion (723). The thin shaft portion (723) has a thinner portion than the output portion (722) from a position facing at least a plurality of spherical bodies (steel balls 65) to a tip on the impact rotary tool (1) side.

According to this embodiment, the thin shaft portion (723) of the input portion (721) has a thinner portion than the output portion (722) from the position facing the multiple spherical bodies (steel balls 65) to the tip on the impact rotary tool (1) side, so that it is difficult for the input portion (721) to come into contact with the multiple spherical bodies (steel balls 65) and it is easy to pull out the connecting shaft (72) from the insertion opening (62).

In the attachment (7; 7a; 7b; 7c) according to the second aspect, in the first aspect, the thin shaft portion (723) is moved from the position facing the plurality of spherical bodies (steel balls 65) to the impact rotary tool ( It is thinner than the output portion (722) because a plurality of recesses (724) are provided toward the tip on the 1) side.

According to this embodiment, it is easy to manufacture a connecting shaft (72) having a thin shaft portion (723) from a rod-shaped body whose width is approximately uniform along the axial direction and in the direction perpendicular to the axial direction.

In the attachment (7; 7a; 7b; 7c) according to the third aspect, in the second aspect, the plurality of recesses (724) are arcuate in plan view from the axial direction of the connecting shaft (72).

According to this aspect, the recess (724) can be aligned with the spherical body (steel ball 65). Therefore, even if the concave portion (724) and the steel ball (65) come into contact, the contact area becomes large, so that the portion in contact with the steel ball 65 is unlikely to be depressed.

In the attachment (7; 7a; 7b; 7c) according to the fourth aspect, in the second or third aspect, the thin shaft portion (723) is located between adjacent recesses (724) in the plurality of recesses (724). It has a protrusion (725) that comes into contact with the inner wall (621) of the insertion port (62).

According to this aspect, the rotational driving force is transmitted from the impact rotary tool (1) also to the thin shaft portion (723) of the input portion (721).

The attachment (7; 7a; 7b; 7c) according to the fifth aspect, in any one of the first to fourth aspects, further includes a housing (70) and an attachment mechanism (8). The housing (70) accommodates at least a portion of the connection shaft (72) and the input shaft (71). The attachment mechanism (8) attaches and fixes the housing (70) to the impact rotary tool (1).

According to this embodiment, the connecting shaft (72) can be easily removed from the insertion opening (62) of the impact rotary tool (1), while the attachment (7; 7a; 7b; 7c) can be fixed to the impact rotary tool (1).

In the attachment (7; 7a; 7b; 7c) according to the sixth aspect, in any one of the first to fifth aspects, the plurality of spherical bodies (steel balls 65) are connected to a pair of opposing spherical bodies (steel balls 65). ), and is movable in a direction perpendicular to the axial direction of the connecting shaft (72). The width (W2) of the portion of the thin shaft portion (723) facing the pair of spherical bodies (steel balls 65) in the direction perpendicular to the connecting shaft (72) is the width (W2) of the portion of the thin shaft portion (723) that faces the pair of spherical bodies (steel balls 65). The distance between the bodies (steel balls 65) is equal to or less than the minimum distance (W1).

According to this aspect, it is possible to almost eliminate pressing of the pair of spherical bodies (steel balls 65) against the input portion (721).

In the attachment (7; 7a; 7b; 7c) according to the seventh aspect, the connection shaft (72) is press-fitted into the input shaft (71) in any one of the first to sixth aspects.

According to this embodiment, the possibility of the connecting shaft (72) falling off or being lost when removing the attachment (7; 7a; 7b; 7c) from the impact rotary tool (1) can be reduced.

The configurations other than the first aspect are not essential to the attachment (7; 7a; 7b; 7c) and can be omitted as appropriate.

The tool system (100) according to the eighth aspect includes an attachment (7; 7a; 7b; 7c) according to any one of the first to seventh aspects, and an impact rotary tool (1) to which the attachment (7; 7a; 7b; 7c) is attached.

According to this aspect, the attachment (7; 7a; 7b; 7c) can be easily removed from the impact rotary tool (1).

1 Impact rotary tool 62 Insertion port 621 Inner wall 65 Steel ball (spherical body)
7, 7a, 7b, 7c Attachment (attachment for impact rotary tool)
70 Housing 71 Input shaft 72 Connection shaft 721 Input part 722 Output part 723 Thin shaft part 724 Recessed part 725 Convex part 100 Tool system

Claims (7)

An impact rotary tool attachment that can be attached to an impact rotary tool,
a connecting shaft that is inserted into an insertion opening of the impact rotary tool, faces each of the plurality of spherical bodies of the impact rotary tool, and transmits rotational driving force from the impact rotary tool;
an input shaft to which the rotational driving force is transmitted from the impact rotary tool via the connection shaft;
Equipped with
The connecting shaft is
an input portion on the side to which the rotational driving force is transmitted from the impact rotary tool in the axial direction of the connection shaft;
an output part extending along the axial direction from the input part and transmitting the rotational driving force to the input shaft;
has
The input portion includes a thin shaft portion in which a plurality of recesses are provided with the same cross section and extend from at least a position facing the plurality of spherical bodies to a tip on the impact rotary tool side.
Attachment for impact rotary tools. The plurality of recesses are arcuate in plan view from the axial direction.
2. The attachment for a rotary impact tool according to claim 1. The thin shaft portion has a convex portion that contacts the inner wall of the insertion port between adjacent concave portions of the plurality of concave portions.
The impact rotary tool attachment according to claim 1 or 2. a casing that accommodates at least a portion of the connection shaft and the input shaft;
an attachment mechanism that attaches and fixes the casing to the impact rotary tool;
further comprising;
The impact rotary tool attachment according to any one of claims 1 to 3. The plurality of spherical bodies are a pair of opposing spherical bodies, and are movable in a direction perpendicular to the axial direction,
a width in the perpendicular direction of a portion of the thin shaft portion facing the pair of spherical bodies is equal to or less than a minimum distance between the pair of spherical bodies in the perpendicular direction;
The impact rotary tool attachment according to any one of claims 1 to 4. the connection shaft is press-fitted into the input shaft;
6. An attachment for a rotary impact tool according to any one of claims 1 to 5. The impact rotary tool attachment according to any one of claims 1 to 6,
an impact rotary tool to which the impact rotary tool attachment is attached;
A tool system with.

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