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EP3978193B1 - Accessoire pour outils rotatifs à impact et système d'outils - Google Patents

Accessoire pour outils rotatifs à impact et système d'outils Download PDF

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Publication number
EP3978193B1
EP3978193B1 EP21199882.8A EP21199882A EP3978193B1 EP 3978193 B1 EP3978193 B1 EP 3978193B1 EP 21199882 A EP21199882 A EP 21199882A EP 3978193 B1 EP3978193 B1 EP 3978193B1
Authority
EP
European Patent Office
Prior art keywords
driving force
output shaft
shaft
input shaft
gear
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP21199882.8A
Other languages
German (de)
English (en)
Other versions
EP3978193A1 (fr
Inventor
Seiji Hashino
Shinji Seko
Hidenori Shimizu
Yasuhiro Yamanaka
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Panasonic Holdings Corp
Original Assignee
Panasonic Holdings Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Panasonic Holdings Corp filed Critical Panasonic Holdings Corp
Publication of EP3978193A1 publication Critical patent/EP3978193A1/fr
Application granted granted Critical
Publication of EP3978193B1 publication Critical patent/EP3978193B1/fr
Active legal-status Critical Current
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B21/00—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose
    • B25B21/02—Portable power-driven screw or nut setting or loosening tools; Attachments for drilling apparatus serving the same purpose with means for imparting impact to screwdriver blade or nut socket
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B23/00—Details of, or accessories for, spanners, wrenches, screwdrivers
    • B25B23/0007—Connections or joints between tool parts

Definitions

  • the present disclosure generally relates to a tool system comprising an attachment for use in impact rotary tools (hereinafter referred to as "impact rotary tool attachment”) , and more particularly relates to a tool system including an impact rotary tool attachment to which rotational driving force is transmitted from an output shaft of an impact rotary tool.
  • JP 2015-020243 A discloses an impact rotary tool attachment for measuring a torque applied to a shaft portion that transmits the impacting force produced by an impact rotary tool to a tip tool.
  • GB 2 260 936 A describes a router attachment that is mounted to a conventional screw gun with a router bit mounted in a chuck.
  • the screwdriver tip and the screwdriver shaft of the screw gun are received in the router housing and drive the input shaft which in turn, via a step-up gear, drives the output shaft and thus the router bit.
  • the output shaft therefore rotates at a higher rate than the input shaft.
  • the router attachment is used in the construction of interior walls and partitions covered in drywall material so that only one tool is needed to both install the screws and to cut the sheets of drywall.
  • US 2005/048884 A1 describes a rotary hand tool attachment that is intended for coupling to a rotary power hand tool of the type that has a housing with a substantially cylindrical nose portion and a motor having an output shaft with a mounting coupling for receiving a drive shaft extending forwardly therefrom.
  • EP 2 933 061 A2 describes an angle impact tool that comprises a handle assembly extending along a first axis and supporting a motor, the motor including a shaft configured to rotate about the first axis, and a work attachment coupled to the handle assembly.
  • EP 0 143 086 A2 describes an equipment or fixture comprising an internal combustion engine, a reduction member or unit coupled to the engine through a friction clutch member, a tool holding assembly drivingly coupled to the reduction unit and ventilating means for cooling the clutch.
  • US 2012/024096 A1 describes a right angle drive including an input shaft, an output shaft, a housing, a pair of input shaft bearings and a pair of output shaft bearings.
  • WO 2010/020097 A1 describes an electric drill multifunctional converter having a shell, a rocking bar that is arranged on the shell through a bearing, wherein one end of said rocking bar is a rotating shaft connected with the mounting hole of the drill head, and the other end has an incline, on which a connecting shaft is provided.
  • US 5 170 545 A describes an adaptor which is designed to be attached to an existing screwgun having a bit with a polygonally shaped end.
  • the adaptor has a recess designed to drivingly receive the hexagonally shaped end of the bit and may be fixedly attached to the existing screwgun.
  • EP 1 094 571 A2 describes an electrical connector crimping tool head comprising a frame and a ram movably connected to the frame.
  • the ram comprises a first member and a second member longitudinally movable along the first member.
  • this expression means that these two directions are substantially perpendicular to each other. That is to say, these two directions may naturally form an angle of exactly 90 degrees between themselves but may also form an angle within 90 ⁇ several degrees (e.g., 90 ⁇ less than 10 degrees) between themselves.
  • a tool system 100 includes an impact rotary tool 1 and an impact rotary tool attachment 7 (hereinafter referred to as an "attachment 7"). As shown in FIG. 2 , the attachment 7 is attached to, and used integrally with, the impact rotary tool 1.
  • the impact rotary tool 1 operates with motive power (such as electric power) supplied from a motive power source such as a battery pack 25. Specifically, as shown in FIG. 3 , a motor 3 supplied with electric power from the battery pack 25 (see FIG. 1 ) turns to transmit rotational driving force to a first output shaft 450. If a tip tool such as a screwdriver bit is attached to the first output shaft 450, a fastener such as a screw as the target of machining work may be attached to the impact rotary tool 1.
  • motive power such as electric power supplied from a motive power source
  • a motor 3 supplied with electric power from the battery pack 25 (see FIG. 1 ) turns to transmit rotational driving force to a first output shaft 450. If a tip tool such as a screwdriver bit is attached to the first output shaft 450, a fastener such as a screw as the target of machining work may be attached to the impact rotary tool 1.
  • the impact rotary tool 1 further includes an impact mechanism 40.
  • the impact mechanism 40 applies, when the load torque of the first output shaft 450 exceeds a predetermined level, impacting force in the direction of rotation to the first output shaft 450. This allows the impact rotary tool 1 to give a greater fastening torque to the workpiece such as a fastener.
  • Examples of such impact rotary tools 1 include an impact wrench, an impact screwdriver, and various other types of tools.
  • the impact rotary tool 1 according to this embodiment is implemented as an impact screwdriver including the first output shaft 450 which may hold a bit such as a screwdriver bit thereon.
  • the attachment 7 is attached to the impact rotary tool 1 as shown in FIG. 2 .
  • the attachment 7 includes an input shaft 71, to which rotational driving force is transmitted from the first output shaft 450 of the impact rotary tool 1, and a second output shaft 73, to which the rotational driving force is transmitted from the input shaft 71 as shown in FIG. 4 .
  • the attachment 7 further includes a driving force conversion mechanism 9 for transmitting the rotational driving force from the input shaft 71 to the second output shaft 73.
  • the driving force conversion mechanism 9 translates, when the rotational driving force is transmitted from the input shaft 71 to the second output shaft 73, the rotational axis Ax0 of the rotation produced by the rotational driving force.
  • the attachment 7 includes the driving force conversion mechanism 9, thus allowing the user to have even a type of machining work, which has been troublesome to do with a known impact rotary tool, done easily.
  • the tool system 100 includes the impact rotary tool 1 and the attachment 7. Also, as shown in FIG. 2 , the attachment 7 is fixed to the impact rotary tool 1 by an attachment mechanism 8 (see FIG. 4 ) of the attachment 7 at a tip portion 211 (see FIG. 1 ) of the impact rotary tool 1.
  • the direction in which a drive shaft 41 (see FIG. 3 ) to be described later and the first output shaft 450 are arranged side by side is hereinafter defined as a forward/backward direction with the first output shaft 450 supposed to be located forward of the drive shaft 41 (i.e., with the drive shaft 41 supposed to be located backward of the first output shaft 450).
  • the direction in which a barrel 21 and a grip portion 22 to be described later are arranged one on top of the other will be hereinafter defined as an upward/downward direction with the barrel 21 supposed to be located upward of the grip portion 22 (i.e., with the grip portion 22 supposed to be location downward of the barrel 21).
  • the impact rotary tool 1 is used in the tool system 100.
  • a rechargeable battery pack 25 is attached removably to the impact rotary tool 1.
  • the impact rotary tool 1 according to this embodiment operates by being powered by the battery pack 25. That is to say, the battery pack 25 is a power supply that supplies a current for driving the motor 3 (see FIG. 3 ).
  • the battery pack 25 is not a constituent element of the impact rotary tool 1.
  • the impact rotary tool 1 may include the battery pack 25 as one of constituent elements thereof.
  • the battery pack 25 includes an assembled battery formed by connecting a plurality of secondary batteries (such as lithium-ion batteries) in series and a case in which the assembled battery is housed.
  • the impact rotary tool 1 includes a body 2, the motor 3, a transmission mechanism 4, and a trigger volume 24.
  • the body 2 houses the motor 3 and a part of the transmission mechanism 4.
  • the body 2 includes the barrel 21, the grip portion 22, and a battery attachment portion 23 as shown in FIG. 2 .
  • the barrel 21 has the shape of a cylinder having an opening at the tip (front end) thereof and a closed bottom at the rear end thereof.
  • the grip portion 22 protrudes downward from the barrel 21.
  • the battery attachment portion 23 is configured such that the battery pack 25 is attachable to, and removable from, the battery attachment portion 23.
  • the battery attachment portion 23 is provided at the tip portion (i.e., at the bottom) of the grip portion 22.
  • the barrel 21 and the battery attachment portion 23 are coupled together via the grip portion 22.
  • the trigger volume 24 protrudes from the grip portion 22.
  • the trigger volume 24 is an operating member for accepting an operating command for controlling the rotation of the motor 3 (see FIG. 3 ).
  • the ON/OFF states of the motor 3 may be switched by pulling the trigger volume 24.
  • the rotational velocity of the motor 3 is adjustable by the manipulative variable indicating how deep the trigger volume 24 has been pulled. Specifically, the greater the manipulative variable is, the higher the rotational velocity of the motor 3 becomes.
  • the motor 3 shown in FIG. 3 may be a brushless motor, for example.
  • the motor 3 includes a rotary shaft 31 and transforms the electric power supplied from the battery pack 25 (see FIG. 2 ) into the rotational driving force to be applied to the rotary shaft 31.
  • the transmission mechanism 4 shown in FIG. 3 is located forward of the motor 3 in the internal space of the barrel 21.
  • the transmission mechanism 4 includes the impact mechanism 40 and a planetary gear mechanism 48.
  • the impact mechanism 40 includes the drive shaft 41, a hammer 42, a return spring 43, an anvil 45, and two steel balls (rolling elements) 49.
  • the rotational driving force of the rotary shaft 31 of the motor 3 is transmitted to the drive shaft 41 via the planetary gear mechanism 48.
  • the drive shaft 41 is provided between the motor 3 and the first output shaft 450.
  • the hammer 42 moves with respect to the anvil 45 to apply rotational impact to the anvil 45 with the motive power supplied from the motor 3.
  • the hammer 42 includes a hammer body 420 and two projections 425 (only one of which is shown in FIG. 3 ).
  • the two projections 425 protrude from one surface, facing the first output shaft 450, of the hammer body 420.
  • the hammer body 420 has a through hole 421, through which the drive shaft 41 is passed.
  • the hammer body 420 has two groove portions 423 on an inner peripheral surface of the through hole 421.
  • the drive shaft 41 has two groove portions 413 on an outer peripheral surface thereof. The two groove portions 413 are connected together.
  • the two steel balls 49 are interposed between the two groove portions 423 and the two groove portions 413. These two groove portions 423, two groove portions 413, and two steel balls 49 together form a cam mechanism. While the two steel balls 49 are moving, the hammer 42 is not only movable along the axis of the drive shaft 41 with respect to the drive shaft 41 but also rotatable with respect to the drive shaft 41. As the hammer 42 moves along the axis of the drive shaft 41 toward, or away from, the anvil 45, the hammer 42 rotates with respect to the drive shaft 41.
  • the anvil 45 includes the first output shaft 450, two impacting portions 451, and a base portion 452.
  • the base portion 452 has a disk shape when viewed in plan in the forward/backward direction.
  • the center of the base portion 452 substantially agrees with the center axis of the drive shaft 41.
  • the first output shaft 450 holds either a tip tool or a coupling shaft 72 (see FIG. 4 ) thereon.
  • the first output shaft 450 has a cylindrical shape and protrudes forward from the base portion 452.
  • the two impacting portions 451 protrude from the base portion 452 along the radius of the base portion 452.
  • the anvil 45 faces the hammer body 420 along the axis of the drive shaft 41.
  • the hammer 42 and the anvil 45 rotate along with each other with the two projections 425 of the hammer 42 and the two impacting portions 451 of the anvil 45 kept in contact with each other in the direction in which the drive shaft 41 rotates.
  • the drive shaft 41, the hammer 42, and the anvil 45 (first output shaft 450) rotate along with each other.
  • the return spring 43 is interposed between the hammer 42 and the planetary gear mechanism 48.
  • the return spring 43 according to this embodiment is configured as a conical coil spring.
  • the impact mechanism 40 further includes a plurality of (e.g., two in the example illustrated in FIG. 3 ) steel balls 50 and a ring 51, both of which are interposed between the hammer 42 and the return spring 43. This makes the hammer 42 rotatable with respect to the return spring 43.
  • the hammer 42 receives, from the return spring 43, force directed toward the first output shaft 450 in the direction aligned with the axis of the drive shaft 41.
  • the movement of the hammer 42 toward the anvil 45 along the axis of the drive shaft 41 will be hereinafter referred to as a "forward movement of the hammer 42.”
  • the movement of the hammer 42 away from the anvil 45 along the axis of the drive shaft 41 will be hereinafter referred to as a “backward movement of the hammer 42.”
  • the impact mechanism 40 starts performing the impacting operation when the load torque becomes equal to or greater than a predetermined value. Specifically, as the load torque increases, the proportion of the component of force that causes the hammer 42 to move backward increases with respect to the force produced between the hammer 42 and the anvil 45. When the load torque becomes equal to or greater than a predetermined value, the hammer 42 starts moving backward while compressing the return spring 43. Then, as the hammer 42 moves backward, the hammer 42 rotates with the two projections 425 of the hammer 42 allowed to go over the two impacting portions 451 of the anvil 45. Thereafter, the hammer 42 is caused to start moving forward upon receiving the force of restitution from the return spring 43.
  • Such a transmission mechanism 4 is housed in the metallic hammer case 400.
  • the hammer case 400 has a circular through hole 402, which is provided through a front surface 401 thereof and allows the first output shaft 450 to pass therethrough.
  • the hammer case 400 also includes a protruding portion 403 protruding forward from a circumferential edge of the through hole 402.
  • the protruding portion 403 has a cylindrical shape.
  • the protruding portion 403 has a plurality of (e.g., two in the example illustrated in FIG. 3 ) recesses 404, which are provided on an outer peripheral surface thereof. As shown in FIG. 4 , pawls 81 of the attachment 7 are engaged with the recesses 404.
  • the first output shaft 450 has an insert hole 62 and a fixing mechanism 63.
  • a tip tool such as a screwdriver bit or the coupling shaft 72 (bar-shaped member) of the attachment 7 is attached.
  • the insert hole 62 according to this embodiment has a regular hexagonal shape when viewed along the axis of the coupling shaft 72 (i.e., in the forward/backward direction).
  • the "regular hexagonal shape” refers to not only a regular hexagon, of which the six sides have exactly the same length and the six interior angles are exactly equal to each other, but also a shape which is similar to, and may be regarded as, a regular hexagon.
  • the transmission mechanism 4 transmits the rotational driving force of the rotary shaft 31 of the motor 3 to the screwdriver bit via the first output shaft 450, thus causing the screwdriver bit to turn.
  • Causing the screwdriver bit to turn while keeping in contact with a fastener (such as a screw) enables machining work such as fastening or loosening the fastener to be performed.
  • the transmission mechanism 4 includes the impact mechanism 40.
  • the impact rotary tool 1 according to this embodiment is an electric impact screwdriver that enables a screw to be fastened while making the impact mechanism 40 perform an impacting operation. The impacting operation applies impacting force to the fastener, such as a screw, via the first output shaft 450.
  • the transmission mechanism 4 transmits the rotational driving force of the rotary shaft 31 of the motor 3 to the coupling shaft 72 via the first output shaft 450. This causes the coupling shaft 72 to turn. Causing the coupling shaft 72 to turn allows the coupling shaft 72 to transmit the rotational driving force to the input shaft 71 of the attachment 7. It will be described later in the "(2.2) Configuration for attachment" section how the attachment 7 operates after the rotational driving force has been transmitted to the input shaft 71.
  • the fixing mechanism 63 includes a plurality of (e.g., two in the example illustrated in FIG. 3 ) holes 64, a plurality of (e.g., two in the example illustrated in FIG. 3 ) steel balls 65 (spherical members), a spring 66, a bit holder 67, and another spring 68.
  • the fixing mechanism 63 is a mechanism for holding a tip tool such as a screwdriver bit with respect to the impact rotary tool 1.
  • the two holes 64 are respectively provided at upper and lower ends of the insert hole 62 so as to be located forward of the tip of the protruding portion 403 of the hammer case 400.
  • Each of the two holes 64 is a hole with the shape of an ellipse, of which the major axis is aligned with the forward/backward direction.
  • the two steel balls 65 are respectively fitted into the two holes 64.
  • the bit holder 67 has the shape of a cylinder, of which the front and rear surfaces are open, and covers the outer periphery of the first output shaft 450 at the tip of the first output shaft 450.
  • the spring 66 is a helical spring covering the outer periphery of the first output shaft 450 between the first output shaft 450 and bit holder 67.
  • the tip tool When a tip tool is inserted into the insert hole 62, the tip tool pushes the two steel balls 65 obliquely upward and obliquely downward, respectively, by overcoming the elastic force of the spring 66. In a state where the tip tool is inserted into the insert hole 62, the two steel balls 65 are allowed to clamp the tip tool between themselves by the elastic force of the spring 66. If the tip tool is provided with a groove to receive the steel balls 65, then the steel balls 65 are fitted into the groove of the tip tool, thereby fixing the tip tool with respect to the impact rotary tool 1.
  • the spring 68 is a helical spring which is 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. Causing the bit holder 67 to move forward against the elastic force applied by the spring 68 leaves a space between the bit holder 67 and the spring 66 in the upward/downward direction between the two holes 64.
  • the steel balls 65 fitted into the groove of the tip tool may be disengaged from the groove by making the two steel balls 65 move into the space.
  • the two (i.e., a pair of) steel balls 65 are movable in both the forward/backward direction and the upward/downward direction.
  • the gap distance as measured in the upward/downward direction between the two steel balls 65 is a minimum gap distance W1.
  • the coupling shaft 72 of the attachment 7 according to this embodiment has no groove into which the steel balls 65 are fitted.
  • the first output shaft 450 is a constituent element for holding a tip tool such as a screwdriver bit. Note that in this embodiment, the tip tool is not one of the constituent elements of the impact rotary tool 1.
  • the attachment 7 includes a housing 70, the input shaft 71, the coupling shaft 72, a second output shaft 73, the attachment mechanism 8, and the driving force conversion mechanism 9.
  • the housing 70 houses the input shaft 71, the coupling 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 coupling shaft 72 couples the first output shaft 450 to the input shaft 71 and drives the first output shaft 450 and the input shaft 71 integrally with each other.
  • the coupling shaft 72 transmits the rotational driving force of the first output shaft 450 from the first output shaft 450 to the input shaft 71.
  • the coupling shaft 72 further includes an input part 721 and an output part 722.
  • the input part 721 is located at one end along the axis of the coupling shaft 72 (i.e., in the forward/backward direction), to which the rotational driving force is transmitted from the impact rotary tool 1.
  • the input part 721 is a part to be inserted into the insert hole 62 of the impact rotary tool 1.
  • the input part 721 has a regular hexagonal prism shape as a whole and has a shape corresponding to that of the insert hole 62 of the impact rotary tool 1.
  • the cross-sectional shape of the input part 721 is the same as the shape of the insert hole 62.
  • the insert hole 62 has a regular hexagonal shape as in this embodiment, then the input part 721 has a regular hexagonal cross-sectional shape and the insert hole 62 also has a regular hexagonal shape.
  • regular hexagonal prism shape refers to not only a regular hexagonal prism, of which the bottom and top surfaces both have a regular hexagonal shape, in which six sides, each connecting a pair of associated vertices of the bottom and top surfaces, have an equal length, and in which those six sides, the bottom surface, and the top surface intersect with each other at right angles, but also a shape which is similar to, and may be regarded as, a regular hexagonal prism as well.
  • the input part 721 has a thinner shaft portion 723.
  • the thinner shaft portion 723 includes a part thinner than the output part 722 in at least a range from a position where the thinner shaft portion 723 faces the two steel balls 65 to one tip located closer to the impact rotary tool 1. As shown in FIG. 4 , the thinner shaft portion 723 includes a part thinner than the output part 722 in a direction in which the thinner shaft portion 723 faces the two steel balls 65. This allows the attachment 7 according to this embodiment to be inserted into, and removed from, the impact rotary tool 1 more easily.
  • the thinner shaft portion 723 is provided with a plurality of recesses 724 (see FIG. 5 ) in the range from the position where the thinner shaft portion 723 faces the two steel balls 65 to the tip located closer to the impact rotary tool 1, and therefore, is thinner than the output part 722.
  • the width W2 between the two (i.e., the pair of) recesses 724 of the thinner shaft portion 723 is smaller than the width W3 of the output part 722.
  • the rest of the input part 721 according to this embodiment has the same shape and the same dimension as the output part 722. That is to say, when measured in the upward/downward direction, the width of the non-thinner shaft portion 723 of the input part 721 is equal to the width W3 of the output part 722.
  • the width W2 between the pair of recesses 724 according to this embodiment is equal to or less than the minimum gap distance W1 (see FIG. 3 ) between the pair of steel balls 65.
  • the width W2 of the part, facing the pair of steel balls 65, of the thinner shaft portion 723 is equal to or less than the minimum gap distance W1 between the pair of steel balls 65.
  • the width W2 is the width of the thinner shaft portion 723 as measured in the direction in which the thinner shaft portion 723 faces the steel balls 65. Since the width W2 between the pair of recesses 724 is equal to or less than the minimum gap distance W1 between the pair of steel balls 65, the thinner shaft portion 723 according to this embodiment may reduce the pressing force applied by the steel balls 65.
  • the thinner shaft portion 723 is provided with the recess 724 in each of the six side surfaces of its regular hexagonal prism.
  • the thinner shaft portion 723 according to this embodiment has six recesses 724.
  • each of the six recesses 724 has the shape of an arc, corresponding to the shape of the steel balls 65, when viewed in plan along the axis of the coupling shaft 72.
  • the thinner shaft portion 723 also has six raised portions 725, each of which is provided between an associated pair of adjacent recesses 724 out of the six recesses 724.
  • each of the six raised portions 725 corresponds to an associated one of the six vertices of the regular hexagon.
  • the output part 722 is a part extended forward in the forward/backward direction from the input part 721 and located on an end of transmitting the rotational driving force to the input shaft 71.
  • the output part 722 according to this embodiment has a regular hexagonal shape corresponding to the shape of the insert hole 711 of the input shaft 71.
  • the cross-sectional shape of the output part 722 is the same as the shape of the insert hole 711. For example, if the output part 722 has a regular hexagonal prism shape as in this embodiment, then the output part 722 has a regular hexagonal cross-sectional shape and the insert hole 711 also has a regular hexagonal shape.
  • the output part 722 according to this embodiment is press-fitted into the insert hole 711 of the input shaft 71.
  • the coupling shaft 72 and the input shaft 71 according to this embodiment are formed integrally with each other and the coupling shaft 72 and the input shaft 71 are driven integrally with each other.
  • the attachment mechanism 8 is used to fix 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 (e.g., two in the example illustrated in FIG. 4 ) pawls 81 and a plurality of (e.g., two in the example illustrated in FIG. 4 ) springs 82.
  • Each of the pawls 81 includes a surface portion 811, a base portion 812, a shaft portion 813, a protruding portion 814, and a hook 816.
  • the surface portion 811 is exposed on the housing 70 and has a rectangular shape when viewed in plan in the upward/downward direction.
  • the base portion 812 protrudes toward the coupling shaft 72 under a rear part of the surface portion 811.
  • the shaft portion 813 is a shaft extending in the rightward/leftward direction and provided for a tip 815, facing the coupling shaft 72, of the base portion 812.
  • the shaft portion 813 is rotatably supported by a bearing 707 provided for the inner walls 701 of the housing 70.
  • the protruding portion 814 protrudes from the back surface (inside surface) of the surface portion 811 toward the coupling shaft 72 and has a cylindrical shape.
  • a helical spring 82 is wound around the outer periphery of the protruding portion 814.
  • the spring 82 is arranged between the surface portion 811 and the inner walls 701 while housing the protruding portion 814 inside.
  • the hook 816 protrudes backward from a rear end, facing the coupling shaft 72, of the base portion 812 and has the shape of a hook.
  • a tip 818 (i.e., either a lower end or an upper end) of the hook 86 is engaged with the recess 404 of the hammer case 400, thus allowing the pawl 81 to fix the housing 70 of the attachment 7 to the impact rotary tool 1.
  • the pawl 81 presses the recess 404 of the hammer case 400 toward the coupling shaft 72 with the elastic force applied by the spring 82.
  • the pawl 81 further includes an operating member 817.
  • the hook 816 moves outward (i.e., away from the coupling shaft 72) around the shaft portion 813.
  • the tip 818 of the hook 816 may be brought out of engagement with the recess 404.
  • the pawl 81 is displaced by the elastic force applied by the spring 82 from a position where the pawl 81 is engaged with the recess 404 to a position where the pawl 81 is disengaged from the recess 404, and vice versa.
  • the input shaft 71 is arranged forward of the coupling shaft 72 such that the center axis of the input shaft 71 substantially agrees with the center axis of the coupling shaft 72. As described above, the input shaft 71 and the coupling shaft 72 are driven integrally with each other and the rotational driving force is transmitted to the input shaft 71 from the coupling shaft 72.
  • the input shaft 71 is supported rotatably by a bearing 702 fixed on 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 with each other.
  • the second gear 92 and the second output shaft 73 are also driven integrally with each other.
  • the driving force conversion mechanism 9 further includes a third gear 93 located in the upward/downward direction between the first gear 91 and the second gear 92.
  • 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 with a plurality of teeth protruding in the radial direction.
  • the first gear 91 and the third gear 93 mesh with each other.
  • the third gear 93 and the second gear 92 mesh with each other.
  • the driving force conversion mechanism 9 further includes a pair of supporting plates 94.
  • the pair of supporting plates 94 is located forward of the tip (front end) of the coupling shaft 72.
  • the pair of supporting plates 94 are provided at an interval larger than the axial length of any of the first gear 91, the second gear 92, or the third gear 93 as measured in the forward/backward direction.
  • the pair of supporting plates 94 rotatably supports the input shaft 71, the shaft 931 of the third gear 93, and the second output shaft 73.
  • the input shaft 71 and the first gear 91 turn integrally with each other.
  • the first gear 91 and the third gear 93 mesh with each other.
  • the third gear 93 to which the rotational driving force has been transmitted from the first gear 91, turns in the opposite direction from the direction in which the first gear 91 turns.
  • the third gear 93 and the second gear 92 also mesh with each other.
  • the 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 has been transmitted from the third gear 93, turns in the opposite direction from the direction in which the third gear 93 turns. That is to say, the second gear 92 turns in the same direction as the first gear 91.
  • the third gear 93 and the second output shaft 73 are driven integrally with each other. Thus, the rotational driving force transmitted to the third gear 93 is transmitted to the second output shaft 73.
  • the driving force conversion mechanism 9 transmits the rotational driving force from the first gear 91 to the second gear 92 indirectly via the third gear 93.
  • the rotational axis Ax1 of the input shaft 71 and the rotational axis Ax2 of the second output shaft 73 are generally parallel to each other. That is to say, the driving force conversion mechanism 9 according to this embodiment translates the rotational axis Ax0 of the rotation produced by the rotational driving force when the rotational driving force is transmitted from the input shaft 71 to the second output shaft 73.
  • the driving force conversion mechanism 9 translates the rotational axis Ax0 of the rotation produced 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 supported rotatably by a bearing 703 fixed on the housing 70 as shown in FIG. 4 .
  • the second output shaft 73 is generally parallel to the input shaft 71 and arranged beside the input shaft 71 in the upward/downward direction and the rightward/leftward direction (i.e., directions perpendicular to the direction aligned with the input shaft 71).
  • the second output shaft 73 has an insert hole 731 and a fixing mechanism 732.
  • a tip tool such as a screwdriver bit is attached into the insert hole 731. If a screwdriver bit is attached to the second output shaft 73, as the second output shaft 73 rotates, the screwdriver bit also rotates along with the second output shaft 73. Causing the screwdriver bit to rotate with the screwdriver bit kept in contact with a fastener (such as a screw) allows a type of machining work such as fastening or loosening the fastener to be done.
  • a fastener such as a screw
  • the fixing mechanism 732 includes a plurality of (e.g., two in the example illustrated in FIG. 4 ) holes 733, a plurality of (e.g., two in the example illustrated in FIG. 3 ) steel balls 734, a spring 735, a bit holder 736, and another spring 737.
  • the two holes 733 are respectively provided at upper and lower ends of the insert hole 731 so as to be located forward of the tip of the housing 70.
  • Each of the two holes 733 is a hole with the shape of an ellipse, of which the major axis is aligned with the forward/backward direction.
  • the two steel balls 734 are respectively fitted into the two holes 733.
  • the bit holder 736 has the shape of a cylinder, of which the front and rear surfaces are open, and covers the outer periphery of the second output shaft 73 in a region forward of the tip of the housing 70.
  • the spring 735 is a helical spring covering the outer periphery of the second output shaft 73 between the second output shaft 73 and bit holder 736.
  • the two steel balls 734 are allowed to clamp the tip tool between themselves in the upward/downward direction by the elastic force of the spring 735. If the tip tool is provided with a groove to receive the steel balls 734, then the steel balls 734 are fitted into the groove of the tip tool, thereby fixing the tip tool with respect to the attachment 7.
  • the spring 737 is a helical spring which is located forward 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.
  • Causing the bit holder 736 to move forward against the elastic force applied by the spring 737 leaves a space between the bit holder 736 and the spring 735 in the upward/downward direction between the two holes 733.
  • the steel balls 734 fitted into the groove of the tip tool may be removed from the groove by making the two steel balls 734 move into the space.
  • 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 coupling shaft 72.
  • the impact mechanism 40 applies impacting force in the rotational direction to the first output shaft 450.
  • This impacting force in the rotational direction, as well as the rotational driving force is transmitted to the second output shaft 73 via the coupling shaft 72, the input shaft 71, the first gear 91, the third gear 93, and the second gear 92.
  • the tool system 100 includes the impact rotary tool 1 and the attachment 7.
  • the attachment 7 includes the input shaft 71, the second output shaft 73, and the driving force conversion mechanism 9 for transmitting the rotational driving force transmitted from the first output shaft 450 of the impact rotary tool 1 from the input shaft 71 to the second output shaft 73.
  • the rotational axis Ax1 of the input shaft 71 and the rotational axis Ax2 of the second output shaft 73 are generally parallel to each other and are not aligned with each other.
  • the driving force conversion mechanism 9 translates the rotational axis Ax0 of the rotation produced by the rotational driving force.
  • the tool system 100 By attaching the attachment 7 for translating the rotational axis Ax0 of the rotation produced by the rotational driving force to the impact rotary tool 1, the tool system 100 according to this embodiment allows the user to have even a type of machining work, which has been troublesome to do with a known impact rotary tool, done easily.
  • the attachment 7 further includes the housing 70 for housing the driving force conversion mechanism 9 at least partially and the attachment mechanism 8 for attaching and fixing the housing 70 onto the tip portion 211 of the impact rotary tool 1.
  • the housing 70 is fixed to the tip portion 211 of the impact rotary tool 1, which is positioned relatively close to the attachment 7. This may reduce the vibrations of the attachment 7 with respect to the impact rotary tool 1. In addition, this may reduce the vibrations of the attachment 7 with respect to the impact rotary tool 1, thus reducing the chances of the driving force conversion by the driving force conversion mechanism 9 being interrupted by the vibrations.
  • the attachment mechanism 8 is attached to a metallic part of the impact rotary tool. Specifically, the attachment mechanism 8 is attached to the hammer case 400 (metallic case) for housing the impact mechanism 40 at least partially.
  • the metallic hammer case 400 will not chip easily. This reduces the chances of the part, to which the attachment mechanism 8 is attached, chipping due to the effect of the impact, for example.
  • the attachment mechanism 8 includes the pawls 81.
  • Each of the pawls 81 is engaged with the recess 404 of the impact rotary tool 1 (hammer case 400). This allows the attachment 7 to be fixed more firmly onto the impact rotary tool 1.
  • the pawl 81 according to this embodiment is engaged with the recess 404 with the elastic force applied by the spring 82, thus allowing the attachment 7 to be fixed even more firmly onto the impact rotary tool 1.
  • the attachment 7 includes the coupling shaft 72.
  • the coupling shaft 72 couples the first output shaft 450 and the input shaft 71 to each other and drives the first output shaft 450 and the input shaft 71 integrally with each other.
  • the coupling shaft 72 transmits the rotational driving force of the first output shaft 450 to the input shaft 71. Since the rotational driving force of the first output shaft 450 may be transmitted indirectly to the input shaft 71, the input shaft 71 and the first output shaft 450 of the impact rotary tool 1 may be designed more flexibly.
  • the driving force conversion mechanism 9 further includes the first gear 91 provided for the input shaft 71 and the second gear 92 provided for the second output shaft 73.
  • the driving force conversion mechanism 9 transmits the rotational driving force indirectly (i.e., via the third gear 93) from the first gear 91 to the second gear 92, thereby transmitting the rotational driving force to the second output shaft 73 that is arranged beside the input shaft 71 in the upward/downward direction and the rightward/leftward direction. That is to say, the driving force conversion mechanism 9 according to this embodiment translates the rotational axis Ax0 of the rotation produced by the rotational driving force transmitted to the input shaft 71. This allows, even when the workpiece such as a fastener is located at a local position, a great fastening torque to be obtained with little pressing force, thus facilitating having the machining work done.
  • the driving force conversion mechanism 9 may be configured to not only translate the rotational axis Ax0 of the rotation produced by the rotational driving force but also change the angle defined by the rotational axis Ax0 and/or convert the rotational driving force into thrust driving force applied along the rotational axis Ax0.
  • the driving force conversion mechanism 9 may include an additional gear, besides the third gear 93, as a member to form a path for transmitting the rotational driving force from the first gear 91 to the second gear 92. That is to say, the driving force conversion mechanism 9 may include four or more gears in order to transmit the rotational driving force from the input shaft 71 to the second output shaft 73.
  • the driving force conversion mechanism 9 does not have to include the third gear 93 but may transmit the rotational driving force directly from the first gear 91 to the second gear 92.
  • the first gear 91 and the second gear 92 are arranged to mesh with each other. Note that if the rotational driving force is transmitted directly from the first gear 91 to the second gear 92, then the direction in which the first gear 91 (input shaft 71) turns becomes opposite from the direction in which the second gear 92 (second output shaft 73) turns.
  • the attachment mechanism 8 does not have to include the spring 82.
  • the hook 816 may be brought into engagement with the recess 404 of the hammer case 400 so that the hook 816 is pressed against the recess 404 with the elastic force of the hook 816 itself, for example.
  • any part other than the hammer case 400 may be made of a metallic material such that the attachment mechanism 8 may be attached thereto.
  • the insert hole 62 does not have to have a regular hexagonal shape.
  • the insert hole 62 may also have any other regular polygonal shape such as an equilateral triangular shape or a square shape.
  • the "regular polygonal shape” refers to not only a “regular polygon” in a strict sense, of which all sides have the same length and all interior angles are equal to each other, but also a shape which is similar to, and may be regarded as, a regular polygon.
  • the insert hole 62 may also have a circular or elliptical shape.
  • the input part 721 does not have to have the shape of a regular hexagonal prism.
  • the input part 721 may also have the shape of any other regular polygonal prism such as an equilateral triangular prism or a square prism.
  • the "regular polygonal prism shape” refers to not only a “regular polygonal prism” in a strict sense, of which the bottom and upper surfaces are the same regular polygon, all sides, each connecting a pair of corresponding vertices of the bottom and upper surfaces, have the same length, and all sides, bottom surface, and upper surface intersect with each other at right angles, but also a shape which is similar to, and may be regarded as, a regular polygonal prism.
  • the input part 721 may also have a circular columnar shape or an elliptical columnar shape.
  • the thinner shaft portion 723 of the coupling shaft 72 does not have to have the recesses 724 and the raised portions 725. As shown in FIG. 7 , a thinner shaft portion 723 according to a variation has no recesses 724 or raised portions 725.
  • the thinner shaft portion 723 according to this variation has a regular hexagonal shape when viewed in plan along the axis of the coupling shaft 72 and has the shape of a regular hexagonal prism extending along the axis of the coupling shaft 72 toward the output part 722.
  • the width W2 of the thinner shaft portion 723 as measured in the upward/downward direction is smaller than the width W3 of the output part 722 as measured in the upward/downward direction.
  • the thinner shaft portion 723 does not have to have the regular hexagonal prism shape but may also have any other regular polygonal prism shape or a circular or elliptical columnar shape.
  • the thinner shaft portion 723 has any arbitrary shape as long as the width W2 thereof as measured in a direction in which the thinner shaft portion 723 faces the steel balls 65 is smaller than the width W3 of the output part 722 as measured in the same direction.
  • the output part 722 does not have to have the regular hexagonal prism shape but may also have any other regular polygonal prism shape or a circular or elliptical columnar shape.
  • the impact rotary tool 1 is implemented as an impact screwdriver, for example. However, this is only an example and should not be construed as limiting. Alternatively, the impact rotary tool 1 may also be implemented as an impact wrench, for example.
  • a tool system 100 according to a second embodiment includes, as shown in FIG. 8 , an attachment 7a for converting the angle defined by the rotational axis Ax0 of the rotation produced by the rotational driving force to be transmitted to the input shaft 71 (see FIG. 9 ), which is a major difference from the tool system 100 according to the first embodiment (see FIG. 4 ).
  • any constituent element of this second embodiment having the same function as a counterpart of the first embodiment described above, will be designated by the same reference numeral as that counterpart's, and description thereof will be omitted as appropriate herein.
  • the attachment 7a includes the housing 70, the input shaft 71, the coupling shaft 72, the second output shaft 73, the attachment mechanism 8, and a driving force conversion mechanism 9a.
  • the input shaft 71 is rotatably supported by a bearing 704 fixed to the housing 70.
  • the second output shaft 73 is positioned to cross the input shaft 71. Specifically, the input shaft 71 extends in the forward/backward direction, while the second output shaft 73 extends in the upward/downward direction.
  • the second output shaft 73 is rotatably supported by bearings 705 and 706 fixed to the housing 70.
  • the driving force conversion mechanism 9a includes a first gear 91a 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 91a and the input shaft 71 are driven integrally with each other.
  • the second gear 92a and the second output shaft 73 are driven integrally with each other.
  • the first gear 91a and the second gear 92a are bevel gears, of which the orientations are different from each other by 90 degrees and which mesh with each other (see FIG. 10 ).
  • the second output shaft 73 and the second gear 92a turn clockwise around the rotational axis Ax3.
  • the rotational axis Ax1 and the rotational axis Ax3 extend in two directions that intersect with each other at right angles.
  • the driving force conversion mechanism 9a changes the angle defined by the rotational axis Ax0 of the rotation produced by the rotational driving force when the rotational driving force is transmitted from the input shaft 71 to the second output shaft 73.
  • the driving force conversion mechanism 9a according to this embodiment changes the angle defined by the rotational axis Ax0 of the rotation produced by the rotational driving force from the angle defined by the rotational axis Ax1 of the input shaft 71 into the angle defined by the rotational axis Ax3 of the second output shaft 73.
  • the angle defined by the rotational axis Ax0 refers to an angle defined by the rotational axis Ax0 with respect to a certain reference axis.
  • the rotational axis Ax1 of the input shaft 71 is used as the reference axis.
  • the driving force conversion mechanism 9a includes: the first gear 91a provided for the input shaft 71; and the second gear 92a provided for the second output shaft 73.
  • the driving force conversion mechanism 9a transmits the rotational driving force from the first gear 91a to the second gear 92a directly, thereby transmitting the rotational driving force to the second output shaft 73 that intersects with the input shaft 71. That is to say, the driving force conversion mechanism 9a according to this embodiment changes the angle defined by the rotational axis Ax0 of the rotation produced by the rotational driving force transmitted to the input shaft 71. This allows, even when the workpiece such as a fastener forms such an angle that makes it difficult to apply force thereto, a great fastening torque to be obtained with little pressing force, thus facilitating having the machining work done easily.
  • the driving force conversion mechanism 9a may also be configured to not only change the angle defined by the rotational axis Ax0 of the rotation produced by the rotational driving force but also translate the rotational axis Ax0 and/or convert the rotational driving force into thrust driving force applied along the rotational axis Ax0.
  • the first gear 91a and the second gear 92a do not have to directly mesh with each other.
  • another gear or any other suitable member may be arranged between the first gear 91a and the second gear 92a such that the rotational driving force is transmitted indirectly from the first gear 91a to the second gear 92a.
  • a tool system 100 according to a third embodiment includes an attachment 7b as shown in FIGS. 11A and 11B , which is a major difference from the tool system 100 according to the first embodiment.
  • the attachment 7b according to this embodiment includes a driving force conversion mechanism 9b for converting the rotational driving force transmitted to the input shaft 71 into thrust driving force applied along the rotational axis Ax0.
  • any constituent element of this third embodiment having the same function as a counterpart of the first embodiment described above, will be designated by the same reference numeral as that counterpart's, and description thereof will be omitted as appropriate herein.
  • the attachment 7b includes the housing 70, the input shaft 71, the coupling shaft 72, a second output shaft 73b, the attachment mechanism 8 (see, for example, FIG. 4 ), a driving force conversion mechanism 9b, a moving blade 74, and a fixed blade 75.
  • the second output shaft 73b has a longitudinal axis extending in a direction aligned with the rotational axis Ax1 of the input shaft 71.
  • the second output shaft 73b and the input shaft 71 are aligned with the rotational axis Ax0 of the rotation produced by the rotational driving force.
  • the second output shaft 73b has the shape of a cylinder having an opening at the rear end thereof and a closed bottom at the front end (tip) thereof.
  • the second output shaft 73b is arranged outside of the outer periphery of the input shaft 71 such that the inner periphery thereof covers the input shaft 71.
  • the second output shaft 73b is supported by the housing 70 so as not to rotate.
  • the driving force conversion mechanism 9b includes a first thread portion 95 and a second thread portion 96.
  • the first thread portion 95 is provided on the outer periphery of the input shaft 71.
  • the second thread portion 96 is provided on the inner periphery of the second output shaft 73b and screwed into the first thread portion 95.
  • the first thread portion 95 and the input shaft 71 rotate integrally with each other.
  • thrust driving force is applied in the forward/backward direction to the second thread portion 96.
  • the driving force conversion mechanism 9b converts the rotational driving force transmitted to the input shaft 71 into thrust driving force applied along the rotational axis Ax0 of the rotation produced by the rotational driving force and transmits the thrust driving force to the second thread portion 96 (the second output shaft 73b).
  • the direction of the thrust driving force transmitted in the forward/backward direction to the second thread portion 96 varies according to the rotational direction of the first thread portion 95. For example, if the first thread portion 95 rotates clockwise around the rotational axis Ax0, forward thrust driving force is transmitted to the second thread portion 96. When the forward thrust driving force is transmitted to the second thread portion 96, the second output shaft 73b moves forward within its movable range. On the other hand, if the first thread portion 95 rotates counterclockwise around the rotational axis Ax0, backward thrust driving force is transmitted to the second thread portion 96. When the backward thrust driving force is transmitted to the second thread portion 96, the second output shaft 73b moves backward within its movable range.
  • the driving force conversion mechanism 9b converts, when transmitting rotational driving force from the input shaft 71 to the second output shaft 73, the rotational driving force into thrust driving force applied along the rotational axis Ax0.
  • the moving blade 74 is a blade moving along with the second output shaft 73b. That is to say, as the second output shaft 73b moves forward, the moving blade 74 moves forward, too. As the second output shaft 73b moves backward, the moving blade 74 moves backward, too.
  • the fixed blade 75 is a blade fixed to the housing 70. A position of the moving blade 74 where the workpiece T1 of cutting may be arranged between the moving blade 74 and the fixed blade 75 as shown in FIG.
  • first position a position of the moving blade 74 where the moving blade 74 and the fixed blade 75 overlap with each other in a direction perpendicular to the rotational axis Ax1 of the input shaft 71 as shown in FIG. 11B will be hereinafter referred to as a "second position.” While the moving blade 74 is being displaced from the first position to the second position with the rotational driving force transmitted to the input shaft 71, the workpiece T1 of cutting is cut off by the moving blade 74 and the fixed blade 75.
  • the driving force conversion mechanism 9b includes: a first thread portion 95 provided for the input shaft 71; and a second thread portion 96 provided for the second output shaft 73 and screwed into the first thread portion 95.
  • the driving force conversion mechanism 9b causes, when the rotational driving force is transmitted from the input shaft 71 to the second output shaft 73, the second thread portion 96 and the second output shaft 73b to move along the rotational axis Ax0 of the rotation produced by the rotational driving force by turning the first thread portion 95 with the rotational driving force transmitted to the input shaft 71.
  • the driving force conversion mechanism 9b converts the rotational driving force into the thrust driving force by causing the second thread portion 96 and the second output shaft 73b to move along the rotational axis Ax0 by turning the first thread portion 95.
  • the attachment 7b converts the rotational driving force to be transmitted to the input shaft 71 into thrust driving force applied along the rotational axis Ax0 of the rotational driving force, thus allowing the user to have a broader variety of machining work done.
  • the load torque of the input shaft 71 is transmitted to the first output shaft 450 via the coupling shaft 72.
  • the impact mechanism 40 applies impacting force in the rotational direction to the first output shaft 450.
  • This impacting force in the rotational direction, as well as the rotational driving force is transmitted to the input shaft 71 via the coupling shaft 72, converted into thrust driving force by the driving force conversion mechanism 9b, and then transmitted to the second output shaft 73b.
  • the workpiece T1 may also be cut off easily with the thrust driving force converted from the impacting force produced by the impact mechanism 40.
  • the attachment 7c may include a moving portion 76 instead of the moving blade 74 according to the third embodiment and a fixed portion 77 instead of the fixed blade 75 according to the third embodiment.
  • the attachment 7c may be used as a pressure bonding attachment for bonding a pair of workpieces together with pressure by clamping the pair of workpieces between the moving portion 76 and the fixed portion 77, for example.
  • the attachment 7c may function as a pressure bonding attachment by converting the rotational driving force to be transmitted to the input shaft 71 into thrust driving force applied along the rotational axis Ax0 of the rotational driving force.
  • the pair of workpieces may be easily pressure-bonded together with the thrust driving force converted from the impacting force produced by the impact mechanism 40.
  • the driving force conversion mechanism 9b may be configured to not only convert the rotational driving force into thrust driving force applied along the rotational axis Ax0 of the rotation produced by the rotational driving force but also translate the rotational axis Ax0 and/or change the angle defined by the rotational axis Ax0.
  • a tool system 100 includes an impact rotary tool attachment 7; 7a; 7b; 7c and an impact rotary tool 1 to which the impact rotary tool attachment 7; 7a; 7b; 7c is attached.
  • the impact rotary tool attachment 7; 7a; 7b; 7c includes an input shaft 71, a second output shaft 73, and a driving force conversion mechanism 9; 9a; 9b.
  • rotational driving force is transmitted from a first output shaft 450 of an impact rotary tool 1.
  • the rotational driving force is transmitted from the input shaft 71.
  • the driving force conversion mechanism 9; 9a; 9b performs, when the rotational driving force is transmitted from the input shaft 71 to the second output shaft 73, at least one operation selected from the group consisting of: translating a rotational axis Ax0 of rotation produced by the rotational driving force; changing an angle defined by the rotational axis Ax0; and converting the rotational driving force into thrust driving force applied along the rotational axis Ax0.
  • the impact rotary tool attachment 7; 7a; 7b; 7c includes the driving force conversion mechanism 9; 9a; 9b.
  • the impact rotary tool attachment 7; 7a; 7b; 7c further includes a housing 70 and an attachment mechanism 8.
  • the housing 70 houses the driving force conversion mechanism 9; 9a; 9b at least partially.
  • the attachment mechanism 8 attaches and fixes the housing 70 onto a tip portion 211 of the impact rotary tool 1.
  • the housing 70 is fixed to the tip portion 211 of the impact rotary tool 1.
  • the tip portion 211 of the impact rotary tool 1 may be positioned relatively close to the impact rotary tool attachment 7; 7a; 7b; 7c, thus reducing the vibrations of the impact rotary tool attachment 7; 7a; 7b; 7c with respect to the impact rotary tool 1.
  • reducing the vibrations of the impact rotary tool attachment 7; 7a; 7b; 7c with respect to the impact rotary tool 1 reduces the chances of the driving force conversion by the driving force conversion mechanism 9; 9a; 9b being interrupted by the vibrations.
  • the attachment mechanism 8 is attached to a metallic part hammer case 400 of the impact rotary tool 1.
  • the impact rotary tool 1 includes: an impact mechanism 40; and a metallic case hammer case 400.
  • the metallic case houses the impact mechanism 40 at least partially.
  • the attachment mechanism 8 is attached to the metallic case.
  • the attachment mechanism 8 may include a pawl 81 to be hooked on the impact rotary tool 1.
  • the pawl 81 may be hooked, by elastic force, on the impact rotary tool 1.
  • the impact rotary tool attachment 7; 7a; 7b; 7c may further include a coupling shaft 72 to couple the first output shaft 450 and the input shaft 71 and to be driven in rotation along with the first output shaft 450 and the input shaft 71.
  • the coupling shaft 72 may transmit the rotational driving force of the first output shaft 450 from the first output shaft 450 to the input shaft 71.
  • a rotational axis Ax1 of the input shaft 71 and a rotational axis Ax2 of the second output shaft 73 may be arranged side by side.
  • the driving force conversion mechanism 9 may include a first gear 91 and a second gear 92.
  • the first gear 91 may be provided for the input shaft 71.
  • the second gear 92 may be provided for the second output shaft 73.
  • the driving force conversion mechanism 9 may translate the rotational axis Ax0 of the rotation produced by the rotational driving force by transmitting the rotational driving force from the first gear 91 to the second gear 92 either directly or indirectly when the rotational driving force is transmitted from the input shaft 71 to the second output shaft 73.
  • a rotational axis Ax1 of the input shaft 71 and a rotational axis Ax3 of the second output shaft 73 may intersect with each other.
  • the driving force conversion mechanism 9a may include a first gear 91a and a second gear 92a.
  • the first gear 91a may be provided for the input shaft 71.
  • the second gear 92a may be provided for the second output shaft 73.
  • the driving force conversion mechanism 9a may change the angle defined by the rotational axis Ax0 of the rotation produced by the rotational driving force by transmitting the rotational driving force from the first gear 91a to the second gear 92a either directly or indirectly when the rotational driving force is transmitted from the input shaft 71 to the second output shaft 73.
  • the input shaft 71 and the second output shaft 73 may be aligned with the rotational axis Ax0 of the rotation produced by the rotational driving force.
  • the driving force conversion mechanism 9b may include a first thread portion 95 and a second thread portion 96.
  • the first thread portion 95 may be provided for the input shaft 71.
  • the second thread portion 96 may be provided for the second output shaft 73 and screwed into the first thread portion 95.
  • the driving force conversion mechanism 9b may convert, when the rotational driving force is transmitted from the input shaft 71 to the second output shaft 73, the rotational driving force into the thrust driving force by causing the second thread portion 96 and the second output shaft 73 to move along the rotational axis Ax0 of the rotation produced by the rotational driving force.
  • the movement of the second thread portion 96 and the second output shaft 73 may be caused when rotation of the first thread portion 95 is produced by the rotational driving force transmitted to the input shaft 71.
  • constituent elements are not essential constituent elements for the impact rotary tool attachment 7; 7a; 7b; 7c but may be omitted as appropriate.

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Claims (7)

  1. Système d'outils (100) comprenant :
    un accessoire d'outil rotatif à impact (7 ; 7a ; 7b ; 7c) ; et
    un outil rotatif à impact (1) auquel l'accessoire d'outil rotatif à impact (7 ; 7a ; 7b ; 7c) est attaché, dans lequel
    l'accessoire d'outil rotatif à impact (7 ; 7a ; 7b ; 7c) comporte :
    un arbre d'entrée (71), auquel une force d'entraînement en rotation est transmise à partir d'un arbre de sortie (450) de l'outil rotatif à impact (1) ;
    un second arbre de sortie (73), auquel la force d'entraînement en rotation est transmise à partir de l'arbre d'entrée (71) ;
    un mécanisme de conversion de force d'entraînement (9 ; 9a ; 9b) configuré pour, lorsque la force d'entraînement en rotation est transmise à partir de l'arbre d'entrée (71) au second arbre de sortie (73), réaliser au moins une opération choisie parmi le groupe constitué de : la translation d'un axe de rotation (Ax0) pour la rotation produite par la force d'entraînement en rotation ; le changement d'un angle défini par l'axe de rotation (Ax0) ; et la rotation de la force d'entraînement en rotation en force d'entraînement de poussée appliquée le long de l'axe de rotation (Ax0) ;
    un logement (70) pour loger le mécanisme de conversion de force d'entraînement (9 ; 9a ; 9b) au moins partiellement ; et
    un mécanisme d'attache (8) configuré pour attacher et fixer le logement (70) sur une partie de pointe (211) de l'outil rotatif à impact (1), et
    l'outil rotatif à impact (1) comportant :
    un mécanisme d'impact (40) ; et
    un boîtier métallique (400) pour loger le mécanisme d'impact (40) au moins partiellement, et
    le mécanisme d'attache (8) étant attaché au boîtier métallique (400), et
    le mécanisme d'impact (40) comportant une enclume (45) et un marteau (42) configuré pour appliquer un impact rotatif à l'enclume (45).
  2. Système d'outils (100) selon la revendication 1, dans lequel
    le mécanisme d'attache (8) comporte un cliquet (81) configuré pour être accroché sur l'outil rotatif à impact (1).
  3. Système d'outils (100) selon la revendication 2, dans lequel
    le cliquet (81) est configuré pour être accroché, par une force élastique, sur l'outil rotatif à impact (1).
  4. Système d'outils (100) selon l'une quelconque des revendications 1 à 3, dans lequel
    l'accessoire d'outil rotatif à impact (7 ; 7a ; 7b ; 7c) comporte en outre :
    un arbre d'accouplement (72) configuré pour accoupler le premier arbre de sortie (450) et l'arbre d'entrée (71) et être entraîné en rotation conjointement avec le premier arbre de sortie (450) et l'arbre d'entrée (71), dans lequel
    l'arbre d'accouplement (72) est configuré pour transmettre la force d'entraînement en rotation du premier arbre de sortie (450) à partir du premier arbre de sortie (450) à l'arbre d'entrée (71).
  5. Système d'outils (100) selon l'une quelconque des revendications 1 à 4, dans lequel
    un axe de rotation (Ax1) de l'arbre d'entrée (71) et un axe de rotation (Ax2) du second arbre de sortie (73) sont agencés côte à côte,
    le mécanisme de conversion de force d'entraînement (9) comporte :
    un premier engrenage (91) fourni pour l'arbre d'entrée (71) ; et
    un second engrenage (92) fourni pour le second arbre de sortie (73), et
    le mécanisme de conversion de force d'entraînement (9) est configuré pour translater l'axe de rotation (Ax0) de la rotation produite par la force d'entraînement en rotation par transmission de la force d'entraînement en rotation à partir du premier engrenage (91) au second engrenage (92) soit directement soit indirectement lorsque la force d'entraînement en rotation est transmise à partir de l'arbre d'entrée (71) au second arbre de sortie (73).
  6. Système d'outils (100) selon l'une quelconque des revendications 1 à 4, dans lequel
    un axe de rotation (Ax1) de l'arbre d'entrée (71) et un axe de rotation (Ax3) du second arbre de sortie (73) se croisent,
    le mécanisme de conversion de force d'entraînement (9a) comporte :
    un premier engrenage (91a) fourni pour l'arbre d'entrée (71) ; et
    un second engrenage (92a) fourni pour le second arbre de sortie (73), et
    le mécanisme de conversion de force d'entraînement (9a) est configuré pour changer l'angle défini par l'axe de rotation (Ax0) de la rotation produite par la force d'entraînement en rotation en transmettant la force d'entraînement en rotation à partir du premier engrenage (91a) au second engrenage (92a) soit directement soit indirectement lorsque la force d'entraînement en rotation est transmise à partir de l'arbre d'entrée (71) au second arbre de sortie (73).
  7. Système d'outils (100) selon l'une quelconque des revendications 1 à 4, dans lequel
    l'arbre d'entrée (71) et le second arbre de sortie (73) sont alignés avec l'axe de rotation (Ax0) de la rotation produite par la force d'entraînement en rotation,
    le mécanisme de conversion de force d'entraînement (9b) comporte :
    une première partie de filetage (95) fournie pour l'arbre d'entrée (71) ; et
    une seconde partie de filetage (96) fournie pour le second arbre de sortie (73) et vissée dans la première partie de filetage (95), et
    le mécanisme de conversion de force d'entraînement (9b) est configuré pour, lorsque la force d'entraînement en rotation est transmise à partir de l'arbre d'entrée (71) au second arbre de sortie (73), convertir la force d'entraînement en rotation en la force d'entraînement de poussée en amenant la seconde partie de filetage (96) et le second arbre de sortie (73) à se déplacer le long de l'axe de rotation (Ax0) de la rotation produite par la force d'entraînement en rotation, le mouvement de la seconde partie de filetage (96) et du second arbre de sortie (73) étant provoqué lorsque la rotation de la première partie de filetage (95) est produite par la force d'entraînement en rotation transmise à l'arbre d'entrée (71).
EP21199882.8A 2020-09-30 2021-09-29 Accessoire pour outils rotatifs à impact et système d'outils Active EP3978193B1 (fr)

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CN114310798A (zh) 2022-04-12
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