EP2712708B1 - Outil de rotation d'impact - Google Patents

Outil de rotation d'impact Download PDF

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Publication number
EP2712708B1
EP2712708B1 EP13184680.0A EP13184680A EP2712708B1 EP 2712708 B1 EP2712708 B1 EP 2712708B1 EP 13184680 A EP13184680 A EP 13184680A EP 2712708 B1 EP2712708 B1 EP 2712708B1
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EP
European Patent Office
Prior art keywords
drive shaft
coupling member
anvil
hole
impact
Prior art date
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Application number
EP13184680.0A
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German (de)
English (en)
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EP2712708A3 (fr
EP2712708A2 (fr
Inventor
Naotake Tanaka
Hiroyuki Tsubakimoto
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 Intellectual Property Management Co Ltd
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Panasonic Intellectual Property Management Co Ltd
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Publication of EP2712708A2 publication Critical patent/EP2712708A2/fr
Publication of EP2712708A3 publication Critical patent/EP2712708A3/fr
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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
    • B25B21/026—Impact clutches

Definitions

  • the present invention relates to an impact rotation tool.
  • An impact rotation tool includes a hammer coupled to a drive shaft, which is rotated and driven by a motor.
  • the hammer impacts an anvil to generate an impact torque used by the impact rotation tool to tighten a screw.
  • Japanese Patent No. 3911905 describes an impact rotation tool that is switched between an impact mode, in which the hammer impacts the anvil, and a drill mode, in which the anvil is rotated integrally with the drive shaft.
  • the '905 patent describes an impact rotation tool 81 that includes an anvil 82, which is coaxial with and rotatable relative to a drive shaft 83.
  • a hammer 84 which includes a hook 84a, is coupled to the drive shaft 83.
  • the hook 84a is engaged with a portion of an arm 82a of the anvil 82.
  • a hammer spring 85 urges the hammer 84 toward the anvil 82.
  • the drive shaft 83 and the hammer 84 (anvil) rotate relative to each other.
  • the drive shaft 83 includes a drive shaft hole 91 having a hexagonal cross-section.
  • the drive shaft hole 91 faces the anvil 82 at a distal end of the drive shaft 83.
  • the anvil 82 includes an anvil hole 92 having a hexagonal cross-section and facing toward the drive shaft 83.
  • a hexagonal coupling member 93 is arranged in the drive shaft hole 91.
  • the coupling member 93 is movable in the axial direction inside the drive shaft hole 91. Further, the coupling member 93 is engaged with one or both of the drive shaft hole 91 and the anvil hole 92.
  • the coupling member 93 is rotatably coupled to a switching shaft 94.
  • the switching shaft 94 moves in the axial direction in cooperation with the movement of a switch (not shown).
  • a stopper 95 is fixed to a distal end of the switching shaft 94 to restrict axial movement of the switching shaft 94 relative to the coupling member 93.
  • the axial movement of the switching shaft 94 axially moves the coupling member 93 in the drive shaft hole 91.
  • the rotation tool 81 is in the impact mode, which permits relative rotation of the drive shaft 83 and the anvil 82 (hammer 84).
  • the rotation tool 81 is in the drill mode, which restricts relative rotation of the drive shaft 83 and the anvil 82 (hammer 84).
  • the drive shaft 83 When, for example, the drive shaft 83 is inclined due to manufacturing or assembling errors of components, a portion of the coupling member 93 may be strongly forced against the wall of the drive shaft hole 91.
  • a regulated clearance is provided between the drive shaft 83 and the anvil 82.
  • the drive shaft 83 moves within the range of the clearance. If a portion of the coupling member 93 is forced strongly against the wall of the drive shaft hole 91, friction would occur where the coupling member 93 contacts the wall of the drive shaft hole 91. This would push the coupling member 93 with a strong force toward the anvil 82. Further, the stopper 95 would repetitively receive a strong force from the coupling member 93. This may shorten the life of the stopper 95.
  • One aspect of the present invention is an impact rotation tool including a drive shaft rotated and driven by a rotational power source.
  • the drive shaft includes a drive shaft hole.
  • An anvil is coaxial with the drive shaft and rotatable relative to the drive shaft.
  • the anvil includes an anvil hole.
  • a hammer is rotated by the drive shaft and engaged with the anvil.
  • the hammer is coupled to the drive shaft so that the hammer moves away from the anvil in an axial direction of the drive shaft when the hammer rotates relative to the drive shaft.
  • An urging member urges the hammer toward the anvil.
  • a switching mechanism switches the impact rotation tool between an impact mode that impacts the anvil with the hammer and a drill mode that integrally rotates the drive shaft and the anvil.
  • the switching mechanism includes a coupling member movable between a position where the coupling member is engaged with a wall of only one of the drive shaft hole and the anvil hole and a position where the coupling member is engaged with the walls of both of the drive shaft hole and the anvil hole.
  • a switching shaft supports the coupling member to be rotatable and moves the coupling member in the axial direction.
  • a stopper restricts axial movement of the coupling member relative to the switching shaft.
  • the switching shaft moves the coupling member to the position where the coupling member is engaged with the wall of only the drive shaft hole to switch to the impact mode.
  • the switching shaft moves the coupling member to the position where the coupling member is engaged with the walls of both of the drive shaft hole and the anvil hole to switch to the drill mode.
  • the wall of the drive shaft hole includes an engagement portion engaged with the coupling member in the impact mode, and a relief formed so as not to contact an outer circumferential surface of the coupling member in the impact mode.
  • the impact rotation tool further includes an elastic member arranged between the coupling member and the stopper.
  • the relief of the drive shaft hole is formed to form a clearance between the coupling member and the drive shaft.
  • the coupling member includes a distal portion and a basal portion; in the drill mode, the distal portion of the coupling member engages with the inner surface of the anvil hole, and the basal portion of the coupling member is engaged with the engagement portion of the drive shaft hole, and the basal portion of the coupling member is engaged with the engagement portion of the drive shaft hole; and in the impact mode, the distal portion of the coupling member is engaged with the engagement portion of the drive shaft hole, and the basal portion of the coupling member is separated from the relief of the drive shaft hole in a radially inner direction.
  • the engagement portion includes an inner diameter substantially equal to an outer diameter of the coupling member, and the relief has an inner diameter that is substantially larger than the outer diameter of the coupling member.
  • the drive shaft includes a distal end supported to be rotatable by the anvil, and the relief is located in the drive shaft hole at a position that is farther from the distal end of the drive shaft than the engagement portion.
  • the present invention provides an impact rotation tool that does not shorten the stopper life.
  • an impact rotation tool 1 is hand-held and may be used as, for example, an impact driver and a drill driver.
  • the impact rotation tool 1 has a T-shaped housing 2 including a cylindrical barrel 2a and a grip 2b, which extends from a lower side of the barrel 2a.
  • the lower end of the grip 2b forms a battery pack seat 2c.
  • a battery pack 3 is attached in a removable manner to the battery pack seat 2c.
  • the grip 2b includes a trigger switch 4 that activates and deactivates the impact rotation tool 1.
  • the longitudinal direction of the barrel 2a is referred to as a front-to-rear direction.
  • a rear portion of the barrel 2a accommodates a motor 5, which serves as a rotational power source.
  • the motor 5 is coupled to a power transmission unit 7, which reduces the speed of the rotation generated by the motor 5 and transmits the rotation to a drive shaft 6.
  • An impact generator 8 is arranged in front of the power transmission unit 7 to generate pulsed torque from the rotation of the drive shaft 6.
  • a chuck 9 that holds a tip tool (not shown) in a removable manner is arranged on the front end of the barrel 2a.
  • the power transmission unit 7 will now be described.
  • the power transmission unit 7 includes a gear case 11, which is fixed to the inner side of the barrel 2a, a speed reduction unit 12, which is accommodated in the gear case 11, and a clutch mechanism 13, which regulates the torque of the motor 5 transmitted to the drive shaft 6 by the speed reduction unit 12.
  • the gear case 11 is cup-shaped and includes an open rear end.
  • a support tube 11b projects toward the front from a front end 11a of the gear case 11.
  • the speed reduction unit 12 is a planetary gear unit including first and second speed reduction mechanisms 12a and 12b arranged in order from the rear, that is, from the motor 5.
  • the motor 5 includes a rotation shaft 5a.
  • the first speed reduction mechanism 12a includes a first sun gear 21a rotated integrally with the rotation shaft 5a of the motor 5.
  • the first speed reduction mechanism 12a includes a plurality of first planet gears 22a engaged with the first sun gear 21a, a first ring gear 23a engaged with the first planet gears 22a, and a first carrier 24a rotatably supporting the first planet gears 22a.
  • the first ring gear 23a is fixed to the gear case 11 so that rotation about the axis of the rotation shaft 5a is prohibited.
  • Each first planet gear 22a is rotatably supported by a first coupling pin 25a on the first carrier 24a. Rotation of the rotation shaft 5a rotates each first planet gear 22a about the axis of the corresponding first coupling pin 25a as the first planet gear 22a orbits about the first sun gear 21a.
  • the first carrier 24a holds a movable carrier 26 with the first coupling pins 25a.
  • the movable carrier 26 is rotatable integrally with the first carrier 24a and movable axially relative to the first carrier 24a.
  • a link 27 connects the movable carrier 26 to a switch 28, which is arranged on the housing 2.
  • the switch 28 is slidable toward the front and rear.
  • the movable carrier 26 moves toward the front and rear in the axial direction in cooperation with the movement of the switch 28.
  • the link 27 is, for example, an arcuate wire spring extending in the circumferential direction.
  • the link 27 is coupled to an annular groove 29 formed in the outer circumferential surface of the movable carrier 26.
  • the second speed reduction mechanism 12b includes a second sun gear 21b arranged integrally with the front surface of the movable carrier 26.
  • the second speed reduction mechanism 12b includes a plurality of second planet gears 22b arranged around and engaged with the second sun gear 21b when the movable carrier 26 (second sun gear 21b) is moved toward the front (refer to Fig. 3 ).
  • the second speed reduction mechanism 12b includes a second ring gear 23b, which is engaged with the second planet gears 22b, and a second carrier 24b, which rotatably supports the second planet gears 22b with second coupling pins 25b.
  • a coupling shaft 31 projecting toward the front is formed integrally with the second sun gear 21b.
  • a through hole 32 axially extends through the coupling shaft 31.
  • the coupling shaft 31 has a front end forming a gear-shaped direct coupling portion 33.
  • a coupling tube 34 which projects toward the front, is formed integrally with the second carrier 24b.
  • the coupling tube 34 includes a rear end that forms a direct coupling portion 35 engaged with the direct coupling portion 33 so as to rotate integrally with the direct coupling portion 33.
  • the second ring gear 23b is rotatably arranged in the gear case 11.
  • the clutch mechanism 13 restricts rotation of the second ring gear 23b when the load torque applied to the second ring gear 23b is less than or equal to a predetermined torque.
  • the load torque is greater than the predetermined torque, the second ring gear 23b rotates freely.
  • the clutch mechanism 13 includes a clutch plate 44, a clutch spring 45, and an adjustment member 46.
  • the clutch spring 45 urges the balls 43 toward the second ring gear 23b with the clutch plate 44.
  • the adjustment member 46 is fastened to the support tube 11b of the gear case 11 and allows for adjustment of the compression amount of the clutch spring 45.
  • the clutch mechanism 13 restricts rotation of the second ring gear 23b. This rotates the second carrier 24b and transmits the output of the speed reduction unit 12 to the drive shaft 6.
  • the second ring gear 23b pushes back the balls 43 and rotates freely.
  • the second carrier 24b is not rotated, and the output of the speed reduction unit 12 is not transmitted to the drive shaft 6.
  • the impact generator 8 will now be described.
  • the impact generator 8 includes the drive shaft 6, an anvil 51, a hammer 52, and a hammer spring 53 serving as an urging member.
  • the anvil 51 is coaxial with the drive shaft 6 and rotatable relative to the drive shaft 6.
  • the hammer 52 is coupled to the drive shaft 6.
  • the hammer spring 53 urges the hammer 52 toward the anvil 51.
  • the axis of the drive shaft 6 extends in the front-to-rear direction.
  • the drive shaft 6 includes a drive shaft hole 54 that opens toward the front, that is, toward the anvil 51.
  • An insertion hole 55 axially extends through the drive shaft 6 and is in communication with the drive shaft hole 54.
  • the axis of the anvil 51 extends in the front-to-rear direction.
  • the anvil 51 includes a front end that receives the basal end of a tip tool.
  • the chuck 9 holds a tip tool so that the tip tool rotates integrally with the anvil 51.
  • the anvil 51 includes a plurality of arms 51a that extend toward the outer side in the radial direction. In the example of Fig. 4 , two arms 51a are arranged at an interval of 180°. As shown in Figs. 2(b) and 3(b) , the anvil 51 includes a support hole 57 that is open at the rear side toward the drive shaft 6. The support hole 57 is coaxial with the drive shaft 6. The anvil 51 includes an anvil hole 58 that is in communication with the support hole 57 and coaxial with the drive shaft hole 54. The front end of the drive shaft 6 is fitted into the support hole 57 and rotatably supported by the anvil 51. An axial clearance is provided between the front end of the drive shaft 6 and the anvil 51 to permit slight axial movement of the drive shaft 6.
  • the hammer 52 is engaged with the anvil 51 when rotated by the drive shaft 6.
  • the hammer 52 is annular. Hooks 52a project toward the front from the front surface of the hammer 52. The rotation of the hammer 52 engages the hooks 52a with the arms 51a of the anvil 51. In the illustrated example, the two hooks 52a, which are trapezoidal, are arranged at an interval of 180°.
  • the hammer spring 53 is held in a compressed state and arranged between the anvil 51 and an annular spring seat 62, which is fixed to the drive shaft 6.
  • the hammer spring 53 is, for example, a coil spring.
  • the hammer 52 moves away from the anvil 51.
  • the hammer 52 is cam-coupled to the drive shaft 6.
  • the outer circumferential surface of the drive shaft 6 includes a cam groove 63 having an inclination angle (lead angle) relative to the axis of the drive shaft 6.
  • the inner circumferential surface of the hammer 52 includes a linear cam groove 64. Balls 65 are held between the cam grooves 63 and 64.
  • the hammer 52 is coupled to the drive shaft 6 with the balls 65 arranged in between.
  • the hammer 52 rotates relative to the drive shaft 6. Further, when the balls 65 roll between the cam grooves 63 and 64, the hammer 52 moves away from the anvil 51 against the urging force of the hammer spring 53. When the hooks 52a move over the arms 51a, the hammer 52 is moved toward the anvil 51 by the urging force of the hammer spring 53 while rotating, and the hammer 52 impacts the arms 51a with the hooks 52a. Such an impact action is intermittently repeated as the drive shaft 6 rotates.
  • the impact generator 8 includes a switching mechanism 71 that switches between an impact mode, in which the hammer 52 impacts the anvil 51, and a drill mode, in which the anvil 51 is rotated integrally with the drive shaft 6.
  • the switching mechanism 71 includes a coupling member 72, a switching shaft 73, and a stopper pin 77.
  • the coupling member 72 is engageable with the walls of one or both of the drive shaft hole 54 and the anvil hole 58.
  • the switching shaft 73 supports the coupling member 72 in a relatively rotatable manner.
  • the switching shaft 73 moves in the axial direction in cooperation with the movement of the switch 28.
  • the stopper pin 77 restricts the axial movement of the coupling member 72 relative to the switching shaft 73.
  • the switching shaft 73 moves the coupling member 72 in the axial direction in accordance with the movement of the switch 28.
  • the switch shaft 73 switches to the impact mode by moving the coupling member 72 to a location where the coupling member 72 is engaged with only the wall of the drive shaft hole 54.
  • the impact mode relative rotation is permitted between the drive shaft 6 and the anvil 51 (hammer 52).
  • the switch shaft 73 switches to the drill mode by moving the coupling member 72 to a location where the coupling member 72 is engaged with the walls of both of the drive shaft hole 54 and the anvil hole 58. In the drill mode, relative rotation is restricted between the drive shaft 6 and the anvil 51 (hammer 52).
  • the coupling member 72 is hexagonal.
  • a fitting hole 74 axially extends through the coupling member 72.
  • the coupling member 72 has an axial length set to be shorter than the drive shaft hole 54, and the coupling member 72 may be completely accommodated in the drive shaft hole 54.
  • the wall of the drive shaft hole 54 includes an engagement portion 75, which is engaged with the coupling member 72 in the impact mode, and a relief 76, which does not contact the outer surface of the coupling member 72 in the impact mode.
  • the engagement portion 75 has a hexagonal cross-section of which inner diameter is substantially the same as the outer diameter of the coupling member 72 (diameter of inscribed circuit of the hexagon formed by the cross-section of the coupling member 72).
  • the relief 76 has a hexagonal cross-section with an inner diameter that is larger than the outer diameter of the coupling member 72.
  • the relief 76 is an annular groove extending in the circumferential direction of the drive shaft 6 and formed in a wall surface of a rear side of the engagement portion 75.
  • the engagement portion 75 is formed in an axial range that allows for the engagement portion 75 to receive the front end of the coupling member 72 during the impact mode and prevent the rear end of the coupling member 72 from entering the relief 76 during the drill mode.
  • the entire anvil hole 58 has a hexagonal cross-section in the axial direction and an inner diameter that is generally the same as the outer diameter of the coupling member 72.
  • the front end of the switching shaft 73 includes a small diameter portion 73a having a smaller diameter than the rear side of the switching shaft 73.
  • the coupling member 72 is rotatably fitted to the small diameter portion 73a.
  • the stopper pin 77 is fixed to the front end of the small diameter portion 73a (end facing the anvil 51).
  • the stopper pin 77 serves as a stopper that is adjacent to the front surface of the coupling member 72.
  • the stopper pin 77 is fixed to the switching shaft 73 in a direction perpendicular to the switching shaft 73.
  • the coupling member 72 is held between a step 73b of the switching shaft 73 and the stopper pin 77 to restrict axial movement of the coupling member 72 relative to the switching shaft 73.
  • the front surface of the coupling member 72 includes a recess 78.
  • An elastic member 79 made of rubber or the like is arranged in the recess 78.
  • the recess 78 is a round hole having a larger diameter than the axial length of the stopper pin 77.
  • the coupling member 72 does not directly contact the stopper pin 77, and the elastic member 79 is arranged between the coupling member 72 and the stopper pin 77.
  • the switching shaft 73 is inserted through the insertion hole 55 of the drive shaft 6 so that the rear end of the switching shaft 73 projects from the drive shaft 6 toward the rear.
  • the rear end of the switching shaft 73 is fitted under pressure into the through hole 32 of the second sun gear 21b.
  • the switching shaft 73 is fixed to the second sun gear 21b to be rotatable integrally with the second sun gear 21b and immovable in the axial direction relative to the second sun gear 21b.
  • the switching shaft 73 moves in the axial direction integrally with the second sun gear 21b (movable carrier 26) in cooperation with the movement of the switch 28.
  • the switch 28 When using the impact rotation tool 1 as an impact driver, the switch 28 is moved toward the rear to move the coupling member 72 with the switching shaft 73 toward the rear. As a result, the coupling member 72 engages with the wall of only the drive shaft hole 54, and the rotation tool 1 enters the impact mode.
  • the coupling member 72 In the example shown in Fig. 2(b) , during the impact mode, the coupling member 72 is completely accommodated in the drive shaft hole 54 and does not enter the anvil hole 58. In the impact mode, the impact torque generated by impact actions rotates the anvil 51 and tightens a screw or the like.
  • the switch 28 When using the impact rotation tool 1 as a drill driver, the switch 28 is moved toward the front to move the coupling member 72 with the switching shaft 73 toward the front. As a result, the coupling member 72 engages with the walls of both of the drive shaft hole 54 and the anvil hole 58, and the rotation tool 1 enters the drill mode. As shown in Fig. 3(b) , in the drill mode, the boundary between the drive shaft 6 and the anvil 51 lies along the coupling member 72. In the drill mode, the torque of the motor 5 is reduced in speed by the speed reduction mechanisms 12a and 12b and transmitted to the drive shaft 6 in order to rotate the anvil 51 and tighten a screw or the like.
  • a regulated clearance in the axial direction is provided between the drive shaft 6 and the anvil 51.
  • the drive shaft 6 moves toward the anvil 51 whenever an impact action is produced.
  • frictional force is produced where the coupling member 72 contacts the drive shaft 6. This pushes the coupling member 72 against the stopper pin 77 in accordance with the frictional force. Due to errors in assembled components or the like, the frictional force produced between the drive shaft 6 and the coupling member 72 may strongly force a portion of the coupling member 72 against the wall of the drive shaft hole 54.
  • the wall of the drive shaft hole 54 in the present embodiment includes the relief 76.
  • the coupling member 72 is not pushed by a strong force.
  • a large force is not applied to the stopper pin 77 by the coupling member 72.
  • the force applied to the stopper pin 77 from the coupling member 72 is absorbed by the elastic deformation of the elastic member 79, which is arranged between the coupling member 72 and the stopper pin 77.
  • the wall of the drive shaft hole 54 includes the engagement portion 75.
  • the coupling member 72 is not rotated relative to the drive shaft 6 in the drive shaft hole 54.
  • the edge of the coupling member 72 does not contact the wall of the drive shaft hole 54, and the application of excessive load to the drive shaft 6 is suppressed.
  • the present embodiment has the advantages described below.
  • a coil spring is used as the hammer spring 53 serving as an urging member that urges the hammer 52 toward the anvil 51.
  • the hammer spring 53 may be a Belleville spring or the like.
  • the stopper does not have to be the stopper pin 77 and may instead be a snap ring or the like.
  • the elastic member 79 which is made of rubber or the like, may be arranged between the coupling member 72 and the stopper pin 77.
  • the relief 76 is an annular groove extending in the circumferential direction of the drive shaft 6 and formed at the rear side of the inner circumferential surface of the engagement portion 75.
  • the relief 76 may be formed by a linear groove extending in the axial direction.
  • a plurality of (six) reliefs 76 are formed at equal angular intervals in the circumferential direction.
  • the drive shaft hole 54, the anvil hole 58, and the coupling member 72 have hexagonal cross-sections.
  • the drive shaft hole 54, the anvil hole 58, and the coupling member 72 may have any non-circular cross-section as long as the rotation of the coupling member 72 may be transmitted to the drive shaft hole 54 and the anvil hole 58.
  • the cross-section may be square, elliptic, or D-shaped.
  • the rotational power source is not limited to the motor 5 and may be, for example, a hydraulic or pneumatic rotational power source.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Portable Nailing Machines And Staplers (AREA)

Claims (6)

  1. Outil rotatif à percussion (1) comprenant :
    un arbre d'entraînement (6) entraîné en rotation et entraîné par une source d'énergie rotative (5), dans lequel l'arbre d'entraînement (6) comprend un trou d'arbre d'entraînement (54) ;
    une enclume (51) qui est coaxiale avec l'arbre d'entraînement (6) et peut tourner par rapport à l'arbre d'entraînement (6), dans lequel l'enclume (51) comprend un trou d'enclume (58) ;
    un marteau (52) entraîné en rotation par l'arbre d'entraînement (6) et mis en prise avec l'enclume (51), dans lequel le marteau (52) est couplé à l'arbre d'entraînement (6) de sorte que le marteau (52) s'éloigne de l'enclume (51) dans une direction axiale de l'arbre d'entraînement (6) lorsque le marteau (52) tourne par rapport à l'arbre d'entraînement (6) ;
    un élément poussée (53) qui pousse le marteau (52) vers l'enclume (51) ; et
    un mécanisme de commutation (71) qui commute l'outil rotatif à percussion (1) entre un mode de percussion qui impacte l'enclume (51) avec le marteau (52) et un mode de perçage qui fait intégralement tourner l'arbre d'entraînement (6) et l'enclume (51), dans lequel le mécanisme de commutation (71) comprend :
    un élément de couplage (72) mobile entre une position dans laquelle l'élément de couplage (72) est mis en prise avec une paroi d'un seul parmi le trou d'arbre d'entraînement (54) et le trou d'enclume (58) et une position dans laquelle l'élément de couplage (72) est mis en prise avec les parois à la fois du trou d'arbre d'entraînement (54) et du trou d'enclume (58),
    un arbre de commutation (73) qui supporte l'élément de couplage (72) à faire tourner et déplace l'élément de couplage (72) dans la direction axiale, et
    une butée (77) qui limite le mouvement axial de l'élément de couplage (72) par rapport à l'arbre de commutation (73) ; et
    dans lequel l'arbre de commutation (73) déplace l'élément de couplage (72) dans la position dans laquelle l'élément de couplage (72) est mis en prise uniquement avec la paroi du trou d'arbre d'entraînement (54) pour passer dans le mode de percussion, et
    dans lequel l'arbre de commutation (73) déplace l'élément de couplage (72) dans la position dans laquelle l'élément de couplage (72) est mis en prise avec les parois à la fois du trou d'arbre d'entraînement (54) et du trou d'enclume (58) pour passer dans le mode de perçage,
    et dans lequel la paroi du trou d'arbre d'entraînement (54) comprend :
    une partie de mise en prise (75) mise en prise avec l'élément de couplage (72) dans le mode de percussion, et
    l'outil rotatif à percussion (1) étant caractérisé en ce que :
    la paroi du trou d'arbre d'entraînement (54) comprend en outre un relief (76) formé afin de ne pas être en contact avec une surface circonférentielle externe de l'élément de couplage (72) dans le mode de percussion.
  2. Outil rotatif à percussion (1) selon la revendication 1, comprenant en outre un élément élastique (79) agencé entre l'élément de couplage (72) et la butée (77).
  3. Outil rotatif à percussion (1) selon la revendication 1 ou 2, dans lequel le relief (76) du trou d'arbre d'entraînement (54) est formé afin de former un jeu entre l'élément de couplage (72) et l'arbre d'entraînement (6).
  4. Outil rotatif à percussion (1) selon l'une quelconque des revendications précédentes, dans lequel :
    l'élément de couplage (72) comprend une partie distale et une partie basale ;
    dans le mode de perçage, la partie distale de l'élément de couplage (72) se met en prise avec la surface interne du trou d'enclume (58) et la partie basale de l'élément de couplage (72) est mise en prise avec la partie de mise en prise (75) du trou d'arbre d'entraînement (54), et la partie basale de l'élément de couplage (72) est mise en prise avec la partie de mise en prise (75) du trou d'arbre d'entraînement (54) ; et
    dans le mode de percussion, la partie distale de l'élément de couplage (72) est mise en prise avec la partie de mise en prise (75) du trou d'arbre d'entraînement (54), et la partie basale de l'élément de couplage (72) est séparée du relief (76) du trou d'arbre d'entraînement (54) dans une direction radialement interne.
  5. Outil rotatif à percussion (1) selon l'une quelconque des revendications précédentes, dans lequel la partie de mise en prise (75) comprend un diamètre interne sensiblement égal à un diamètre externe de l'élément de couplage (72), et
    le relief (76) a un diamètre interne qui est sensiblement supérieur au diamètre externe de l'élément de couplage (72).
  6. Outil rotatif à percussion (1) selon l'une quelconque des revendications précédentes, dans lequel l'arbre d'entraînement (6) comprend une extrémité distale supportée pour être entraînée en rotation grâce à l'enclume (51), et
    le relief (76) est positionné dans le trou d'arbre d'entraînement (54) dans une position qui est plus éloignée de l'extrémité distale de l'arbre d'entraînement (6) que la partie de mise en prise (75).
EP13184680.0A 2012-09-28 2013-09-17 Outil de rotation d'impact Active EP2712708B1 (fr)

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JP2012216027A JP5963050B2 (ja) 2012-09-28 2012-09-28 インパクト回転工具

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EP2712708A2 EP2712708A2 (fr) 2014-04-02
EP2712708A3 EP2712708A3 (fr) 2018-03-21
EP2712708B1 true EP2712708B1 (fr) 2019-02-06

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US11565394B2 (en) * 2019-10-28 2023-01-31 Snap-On Incorporated Double reduction gear train

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Publication number Priority date Publication date Assignee Title
US3952814A (en) * 1975-03-14 1976-04-27 Mikhail Lvovich Gelfand Impact wrench
JP3372345B2 (ja) * 1993-05-26 2003-02-04 松下電工株式会社 インパクト回転工具
CN1145843A (zh) * 1996-07-18 1997-03-26 丁心河 拆装重型汽车轮胎12伏自动击发电扳机
JP3911905B2 (ja) * 1999-04-30 2007-05-09 松下電工株式会社 インパクト回転工具
JP4468786B2 (ja) * 2004-10-28 2010-05-26 株式会社マキタ インパクト工具
US20060237205A1 (en) * 2005-04-21 2006-10-26 Eastway Fair Company Limited Mode selector mechanism for an impact driver
US7410007B2 (en) * 2005-09-13 2008-08-12 Eastway Fair Company Limited Impact rotary tool with drill mode
EP2815850B1 (fr) * 2007-02-23 2016-02-03 Robert Bosch Gmbh Outil d'alimentation rotatif qui fonctionne en mode d'impact ou en mode de forage
JP5382291B2 (ja) * 2008-05-08 2014-01-08 日立工機株式会社 オイルパルス工具
US9193053B2 (en) * 2008-09-25 2015-11-24 Black & Decker Inc. Hybrid impact tool
JP4674640B2 (ja) * 2009-01-27 2011-04-20 パナソニック電工株式会社 インパクト回転工具
JP4636188B2 (ja) * 2009-01-27 2011-02-23 パナソニック電工株式会社 切替操作装置

Non-Patent Citations (1)

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None *

Also Published As

Publication number Publication date
JP5963050B2 (ja) 2016-08-03
EP2712708A3 (fr) 2018-03-21
JP2014069262A (ja) 2014-04-21
CN103707253A (zh) 2014-04-09
CN103707253B (zh) 2016-01-27
EP2712708A2 (fr) 2014-04-02

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