WO2016017545A1 - 打撃工具 - Google Patents
打撃工具 Download PDFInfo
- Publication number
- WO2016017545A1 WO2016017545A1 PCT/JP2015/071124 JP2015071124W WO2016017545A1 WO 2016017545 A1 WO2016017545 A1 WO 2016017545A1 JP 2015071124 W JP2015071124 W JP 2015071124W WO 2016017545 A1 WO2016017545 A1 WO 2016017545A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- hammer
- claws
- claw
- spindle
- anvil
- Prior art date
Links
- 210000000078 claw Anatomy 0.000 claims description 261
- 229910000831 Steel Inorganic materials 0.000 claims description 65
- 239000010959 steel Substances 0.000 claims description 65
- 230000007246 mechanism Effects 0.000 description 36
- 239000004519 grease Substances 0.000 description 27
- 239000003638 chemical reducing agent Substances 0.000 description 12
- 230000033001 locomotion Effects 0.000 description 11
- 230000002093 peripheral effect Effects 0.000 description 11
- 238000005096 rolling process Methods 0.000 description 8
- 230000000694 effects Effects 0.000 description 5
- 230000009467 reduction Effects 0.000 description 5
- 238000010586 diagram Methods 0.000 description 3
- 239000002023 wood Substances 0.000 description 3
- 230000007774 longterm Effects 0.000 description 2
- 239000000314 lubricant Substances 0.000 description 2
- 238000013459 approach Methods 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 239000003502 gasoline Substances 0.000 description 1
- 239000003915 liquefied petroleum gas Substances 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000004033 plastic Substances 0.000 description 1
- 238000000638 solvent extraction Methods 0.000 description 1
Images
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
-
- 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
Definitions
- the present invention relates to a striking tool including a striking member that converts a rotational force of a rotating member into a rotational force and a striking force of an output member.
- Patent Document 1 An example of a striking tool including a striking member that converts a rotational force of a rotating member into a rotational force and a striking force of an output member is described in Patent Document 1.
- the striking tool described in Patent Document 1 includes a hammer (striking member) that converts the rotational force of a spindle (rotating member) into the rotational force and striking force of an anvil (output member).
- a pair of spindle cams are provided on the outer peripheral portion of the spindle, and a pair of hammer cams are provided on the inner peripheral portion of the hammer, and steel balls are respectively disposed between these cams.
- Two hammer claws arranged at equal intervals in the circumferential direction are provided on the anvil side of the hammer, and two anvil claws arranged at equal intervals in the circumferential direction are provided on the hammer side of the anvil. These hammer claws and anvil claws are engaged with each other, whereby the rotational force of the hammer is transmitted to the anvil.
- a tip tool such as a driver bit is attached to the side opposite to the hammer side along the axial direction of the anvil.
- the steel ball rolls following the spindle cam and the hammer cam.
- the hammer moves away from the anvil against the spring force of the coil spring, and then approaches the anvil by the spring force of the coil spring.
- the hammer rotates relative to the anvil when separated from the anvil, and the hammer pawl and the anvil pawl engage with each other and collide when approaching the anvil.
- the hammer claw and the anvil claw are repeatedly released and engaged, whereby a striking force in the rotational direction is generated on the tip tool.
- FIGS. 16 and 17 are explanatory views for explaining the positional relationship between the hammer claw and the anvil claw of the conventional impact tool.
- two hammer cams 101a and 101b are provided on the inner peripheral portion of the hammer 100, and the anvil side (front side in the figure) of the hammer 100 is provided.
- Two hammer claws 102a and 102b are disposed at portions corresponding to the central portion CP of the two hammer cams 101a and 101b along the circumferential direction of the hammer 100 so as to face each other with the axis HC of the hammer 100 as a center.
- the hammer pawl 102a of the hammer 100 collides with the anvil pawl 105a of the anvil 104 to generate the striking force F1
- the hammer pawl 102b collides with the anvil pawl 105b.
- a striking force F3 is generated. Since these striking forces are generated at the same time, the axial center HC of the hammer 100 and the axial center SC of the spindle 103 do not deviate, and galling is unlikely to occur.
- a configuration in which the two hammer claws 102a and 102b are located at the wall portion between the hammer cams 101a and 101b is also conceivable.
- the reaction force of the striking force generated by the collision Is strongly pressed against the inner central portion of the hammer cam 101 a via the spindle 103.
- the central part of the hammer cam 101a on the radially inner side of the hammer 100 is a portion (hammer cam bottom) having the smallest contact area with the spindle 103. Therefore, the surface pressure per unit area in the inner central part is large, and therefore the galling phenomenon is likely to occur.
- a predetermined amount of grease is applied to the spindle cam and the hammer cam in order to make the rolling of the steel ball smooth. That is, grease is filled in the hammer case that accommodates the hammer.
- a relatively large opening through which the steel ball can be viewed is provided at the axial end of the hammer cam.
- the hitting tool described in Patent Document 1 has a structure in which grease adhering to the steel ball, the spindle cam, and the hammer cam easily leaks to the outside due to vibration during the hitting operation.
- grease leaks to the outside smooth rolling of the steel ball becomes difficult, and as a result, a problem may occur that the spindle cam, the hammer cam, and further the steel ball are worn early.
- An object of the present invention is to provide a striking tool that can suppress the caulking phenomenon between a striking member and a rotating member even when a turning force is applied to the striking tool.
- the objective of this invention is providing the impact tool which can suppress that the grease adhering to the steel ball leaks outside the cam groove.
- an impact tool that applies rotational force and impact force to a tip tool, the motor, a spindle rotated by the motor, an anvil to which the tip tool is attached, and the rotational force of the spindle.
- a hammer that converts the rotating force and the striking force of the anvil into a second claw that engages with the first claw of the anvil, a through-hole through which the spindle passes, and a diameter of the through-hole.
- the second claw is provided between the bottom portion and the wall portion in the circumferential direction of the through hole.
- the top portion of the second claw provided in the central portion in the circumferential direction on the radially inner side is located between the bottom portion and the wall portion.
- a plurality of the second claws are provided, and at least one of the plurality of second claws is provided between the bottom portion and the wall portion.
- three first claws and three second claws are provided.
- an impact tool that imparts rotational force and impact force to a tip tool, the motor, a spindle rotated by the motor, an anvil to which the tip tool is attached, and the rotational force of the spindle
- a hammer that converts the rotational force and the striking force of the anvil into a second pawl that engages with the first pawl of the anvil, a through-hole through which the spindle passes, and a through-hole of the through-hole.
- a plurality of the second claws are provided, and a central portion in the circumferential direction of at least one of the plurality of second claws is located in a region of the one inclined portion, and the first claw When the one claw and the second claw are engaged, the spindle is pressed against the other inclined portion.
- three first claws and three second claws are provided.
- an impact tool for imparting rotational force and impact force to a tip tool comprising a motor, a spindle rotated by the motor, and a first claw, wherein the tip tool is disposed on the front side.
- the first claw is configured to overlap the bottom portion of the cam groove when viewed from the axial direction.
- a plurality of the first claws are provided, and at least one of the plurality of first claws overlaps the bottom portion.
- the first claw overlaps the steel ball when viewed from the axial direction of the rotating member under a state in which the first claw and the second claw are engaged.
- three first claws and three second claws are provided.
- the present invention when the first claw and the second claw are engaged to perform a striking operation, leakage of grease attached to the steel ball to the outside can be suppressed. Thereby, stable operation over a long period of time can be realized.
- FIG. 3 is an exploded perspective view of the striking mechanism according to the first embodiment.
- (A) is a perspective view of a hammer
- (b) is a developed view of a through hole. It is an expanded sectional view explaining the retraction operation
- (A), (b) is operation
- FIG. (A), (b), (c) is operation
- FIG. 10 is a development view of a through hole of a hammer according to a fourth embodiment.
- (A), (b) is operation
- FIGS. 11A and 11B are diagrams corresponding to FIG. 11 illustrating the striking mechanism according to the fifth embodiment.
- FIG. 10 is an exploded perspective view of a striking mechanism according to a sixth embodiment.
- (A), (b) is operation
- FIG. It is explanatory drawing explaining the positional relationship of the hammer nail
- FIG. 1 is a perspective view showing the impact tool of the present invention
- FIG. 2 is a partial sectional view of the impact tool of FIG. 1
- FIG. 3 is an exploded perspective view of the impact mechanism of Embodiment 1
- FIG. 5B is a developed view of the through hole
- FIG. 5 is an enlarged sectional view for explaining the retreating operation of the hammer
- FIGS. 6A and 6B are views of the striking mechanism of FIG. The operation
- an impact driver 10 as an impact tool includes a battery pack 11 that houses a battery cell that can be charged and discharged, and an electric motor 12 that is driven by power supplied from the battery pack 11. And.
- the electric motor 12 is a drive source that converts electrical energy into kinetic energy.
- the impact driver 10 includes a casing 13 made of plastic or the like, and the electric motor 12 is provided inside the casing 13 (housing).
- the electric motor 12 includes a rotating shaft 14 that rotates about an axis A.
- the rotary shaft 14 is rotated in the forward direction or the reverse direction by operating the trigger switch 15. That is, by operating the trigger switch 15, power is supplied from the battery pack 11 to the electric motor 12.
- the rotation direction of the rotary shaft 14 can be switched by operating a forward / reverse switching lever 16 provided in the vicinity of the trigger switch 15.
- the impact driver 10 includes an anvil (output member) 18 that supports a tip tool 17 such as a driver bit on the tip side (front side) thereof.
- the anvil 18 is rotatably supported by a sleeve 19 mounted inside the casing 13 (hammer case). Note that grease (not shown) is applied to the inside of the sleeve 19 to smooth the rotation of the anvil 18.
- the anvil 18 rotates about the axis A, and a tip tool 17 is detachably provided at a tip portion of the anvil 18 via an attaching / detaching mechanism 20.
- a reduction gear 21 is provided in the casing 13 (hammer case) and between the electric motor 12 and the anvil 18 in the direction along the axis A.
- the speed reducer 21 is a power transmission device that transmits the rotational force of the electric motor 12 to the anvil 18, and the speed reducer 21 is configured by a so-called single pinion type planetary gear mechanism.
- the speed reducer 21 includes a sun gear 22 disposed coaxially with the rotary shaft 14, a ring gear 23 disposed so as to surround the sun gear 22, and a plurality of planetary gears 24 meshed with both the sun gear 22 and the ring gear 23, It has the carrier 25 which supports each planetary gear 24 so that rotation and revolution are possible.
- the ring gear 23 is fixed to the casing 13 (hammer case) and cannot rotate.
- the carrier 25 is integrally provided with a spindle (rotating member) 26 that rotates about the axis A together with the carrier 25. That is, the rotating shaft 14, the speed reducer 21, the spindle 26, and the anvil 18 of the electric motor 12 are respectively arranged around the axis A.
- the spindle 26 is provided between the anvil 18 in the direction along the axis A and the speed reducer 21, and a shaft portion 26 a protruding in the direction along the axis A is formed at the tip portion of the spindle 26 on the anvil 18 side. ing.
- a holder member 27 formed in a substantially bowl shape is provided inside the casing 13 (housing) and between the electric motor 12 and the speed reducer 21 in the direction along the axis A.
- a bearing 28 is attached to the center portion of the holder member 27, and the bearing 28 rotatably supports a proximal end portion of the spindle 26 on the electric motor 12 side.
- a pair of (two) groove-shaped spindle cams 26b1 and 26b2 are provided on the outer peripheral portion of the spindle 26 on the anvil 18 side. Approximately half of the steel ball (steel ball) 29 enters the spindle cams 26b1 and 26b2.
- the spindle cams 26b1 and 26b2 are also coated with grease (not shown) for smooth rolling of the steel balls 29. That is, a casing 13 (a space formed by the hammer case and the holder member 27) that houses a hammer 30 described later is filled with grease as a lubricant.
- a holding hole 18a coaxial with the axis A is provided at the base end portion of the anvil 18 on the spindle 26 side.
- a shaft portion 26a of the spindle 26 is rotatably inserted into the holding hole 18a. That is, the anvil 18 and the spindle 26 are relatively rotatable about the axis A. Note that grease (not shown) is also applied between the shaft portion 26a and the holding hole 18a so as to make the relative rotation of both of them smooth.
- the anvil 18 is provided with a mounting hole 18b coaxially with the axis A.
- the mounting hole 18b is opened toward the outside of the casing 13 (hammer case), and is provided for attaching and detaching the proximal end portion of the tip tool 17.
- a hammer (striking member) 30 formed in a substantially annular shape is provided around the spindle 26.
- the hammer 30 is disposed between the speed reducer 21 and the anvil 18 in the direction along the axis A (the rear side of the anvil 18).
- the hammer 30 is rotatable relative to the spindle 26 and is relatively movable in the direction along the axis A.
- FIG. 2 shows a state in which the hammer 30 has moved to the most front side (anvil 18 side). At this time, the steel ball 29 described later is positioned at the bottom of the rearmost side (anti-anvil 18 side) in the direction along the axis A of the hammer cams 30a1 and 30a2 described later.
- a pair of (two) groove-shaped hammer cams (cam grooves) 30 a 1 and 30 a 2 extending in the direction along the axis A are formed on the inner peripheral portion of the hammer 30. Approximately half of the steel ball 29 is inserted into the hammer cams 30a1 and 30a2. The hammer cams 30a1 and 30a2 are also coated with grease (not shown) for smooth rolling of the steel balls 29.
- one steel ball 29 is held with the spindle cam 26b1 and the hammer cam 30a1 as one set. Further, the spindle cam 26b2 and the hammer cam 30a2 constitute a set, and the other steel ball 29 is held.
- the steel ball 29 is formed of a metal rolling element. Therefore, the hammer 30 can move in the direction along the axis A within a range in which the steel ball 29 can roll with respect to the spindle 26. Further, the hammer 30 is movable in the circumferential direction about the axis A within a range in which the steel ball 29 can roll with respect to the spindle 26.
- An annular plate 31 made of a steel plate is provided around the spindle 26 and between the reducer 21 and the hammer 30 in the direction along the axis A.
- a coil spring 32 is provided in a compressed state between the annular plate 31 and the hammer 30 in the direction along the axis A.
- the carrier 25 is restricted from moving in the direction along the axis A by contacting the bearing 28 and the holder member 27, and the pressing force of the coil spring 32 is applied to the hammer 30. Thereby, the hammer 30 is pushed toward the anvil 18 in the direction along the axis A by the pressing force of the coil spring 32.
- An annular stopper 33 is provided around the spindle 26 and inside the annular plate 31 in the radial direction.
- the stopper 33 is formed of an elastic body such as rubber and is attached to the spindle 26.
- the stopper 33 regulates the amount of movement of the hammer 30 toward the reduction gear 21 along the axis A.
- the striking mechanism SM for imparting striking force to the tip tool 17 is formed by the spindle 26, the hammer 30, the anvil 18, the steel ball 29 and the coil spring 32.
- the second claws 30e1 and 30e2 (hammer claws) of the hammer 30 and the first claws 18d1 and 18d2 (anvil claws) of the anvil 18 both refer to FIG. 3.
- the opening and engagement are repeated at a high speed, thereby generating a striking force on the tip tool 17.
- the weight of the hammer 30 is set to be larger than the weight of the anvil 18, and the hammer 30 transmits the rotational force of the spindle 26 to the anvil 18 and strikes the rotational force of the spindle 26 in the rotational direction of the anvil 18. Convert to force.
- the weight of the hammer 30 may be set smaller than the weight of the anvil 18.
- the hammer 30 includes a main body portion 30b formed in a substantially cylindrical shape.
- a through hole 30c is provided on the inner side in the radial direction of the main body 30b so as to extend in the direction along the axis A and through which the spindle 26 can turn.
- the anvil 18 side of the main body 30b is tapered. That is, the spindle 26 side of the main body 30b has a large diameter, and the anvil 18 side of the main body 30b has a small diameter.
- the diameter dimension of the main body 30b on the spindle 26 side (large diameter side) is set to about 40 mm.
- an opposing flat surface 30d that faces the anvil 18 is provided.
- the opposing flat surface 30d is integrally provided with two second claws 30e1 and 30e2 protruding in the direction along the axis A and toward the anvil 18 side.
- These second claws 30e1 and 30e2 are arranged at intervals of 180 degrees along the circumferential direction of the opposing plane 30d, and the cross-sectional shape along the direction intersecting the axis A is substantially a sector shape.
- the tip end side of the second pawls 30e1 and 30e2 that is tapered, that is, the radially inner side of the sector, is directed to the radially inner side of the hammer 30, that is, the through hole 30c.
- a first contact plane SF1 is provided on one side of the second claws 30e1 and 30e2 along the circumferential direction of the hammer 30.
- a second contact plane SF2 is provided on the other side of the second claws 30e1 and 30e2 along the circumferential direction of the hammer 30. Then, the first contact plane SF1 is in contact with a fourth contact plane SF4 of first claws 18d1 and 18d2 of the anvil 18, which will be described later, and the second contact plane SF2 is in contact with the first claws 18d1 of the anvil 18.
- the third contact plane SF3 of 18d2 comes into contact with substantially the entire surface.
- the width dimension of the second claws 30e1 and 30e2 in the direction outside the hammer 30 in the radial direction and along the circumferential direction is set to about 15 mm. Accordingly, the first claws 18d1 and 18d2 of the anvil 18 can enter with sufficient margin between the second claws 30e1 and 30e2 adjacent in the circumferential direction of the hammer 30.
- a pair of hammer cams (cam grooves) 30a1 and 30a2 are provided in the inner peripheral portion of the hammer 30, that is, the through hole 30c so as to face each other with the through hole 30c as a center.
- the hammer cams 30a1 and 30a2 are provided to be recessed radially outward with respect to the through hole 30c, and the depth dimension along the radial direction of the hammer cams 30a1 and 30a2 is substantially equal to the radial dimension of the steel ball 29.
- the hammer cams 30a1 and 30a2 are both formed in the same shape, and arc portions 40a are provided at the central portions CP of the hammer cams 30a1 and 30a2 along the circumferential direction of the through hole 30c.
- the position of the center of the arc portion 40a in the circumferential direction is substantially coincident with the position of the central portion CP. That is, the central portion CP along the circumferential direction of the hammer cams 30a1 and 30a2 is the rearmost end of the hammer cams 30a1 and 30a2 in the axial direction of the through hole 30c (the lowermost portion of the hammer cams in FIG. 4B).
- the arc portion 40 a is disposed on the speed reducer 21 side (lower side in the figure) along the axial direction of the hammer 30.
- inclined portions 40b extending toward the anvil 18 side (upper side in the drawing) along the axial direction of the hammer 30 are provided on both sides of the arc portion 40a along the circumferential direction of the through hole 30c.
- the linear part 40c extended in the axial direction of the hammer 30 (through-hole 30c) is provided in the opposite side to the circular arc part 40a side of each inclination part 40b, respectively.
- the respective arc portions 40a are made of steel.
- Each of the balls 29 is positioned.
- the dimension along the axial direction of the through hole 30c is large, that is, radially outward with respect to the through hole 30c.
- a wall portion 30c1 that is not recessed is provided.
- Two wall portions 30c1 are provided at positions shifted by approximately 180 degrees in the circumferential direction of the through hole 30c, and have a function of partitioning the two hammer cams 30a1 and 30a2.
- a portion having the central portion CP (hammer cam top portion) of the hammer cams 30a1 and 30a2 along the circumferential direction of the through hole 30c and a portion corresponding to the arc portion 40a has a small size along the axial direction of the through hole 30c.
- 30c2 is provided.
- Two bottom portions 30c2 are provided at positions shifted by approximately 180 degrees in the circumferential direction of the through hole 30c.
- the dimension of the bottom part 30c2 along the axial direction of the through hole 30c is set to be approximately 1/7 of the dimension of the wall part 30c1 along the axial direction of the through hole 30c.
- the width dimension of the bottom part 30c2 along the circumferential direction of the through hole 30c is substantially the same as the width dimension of the wall part 30c1 along the circumferential direction of the through hole 30c on one end side in the axial direction of the through hole 30c (on the reduction gear 21 side). The same dimensions are set.
- the width dimension of the wall portion 30c1 on the other axial end side (anvil 18 side) of the through hole 30c and along the circumferential direction of the through hole 30c is substantially the width dimension of the bottom portion 30c2 along the circumferential direction of the through hole 30c.
- the dimension is set to 1/4.
- a symbol BP in FIG. 4B indicates a central portion of the wall portion 30c1 along the circumferential direction of the through hole 30c.
- the wall 30c1 and the bottom 30c2 are connected between the wall 30c1 and the bottom 30c2 along the circumferential direction of the through hole 30c, and an inclined portion (trapezoid-shaped portion formed in a substantially trapezoidal shape in a portion corresponding to the inclined portion 40b. ) 50 (shaded portion in the figure) is provided.
- the inclined portion 50 is provided in two places (four places in total) symmetrically with respect to the respective central portions CP (hammer cam top portions) of the hammer cams 30a1 and 30a2 in the circumferential direction of the through hole 30c.
- the wall portions 30c1, the inclined portion 50, the bottom portion 30c2, the inclined portion 50, and the wall portion 30c1 are formed side by side along the circumferential direction of the through hole 30c to constitute the hammer cams 30a1 and 30a2.
- a bottom portion 30c2, an inclined portion 50, and a wall portion 30c1 are provided in order from the central portion CP side symmetrically with respect to the central portion CP (hammer cam top portion) of the hammer cams 30a1 and 30a2.
- the inclined portion 50 is a pressing portion (see FIG.
- the surface area of the inclined part 50 is set larger. This means that the inclined portion 50 can disperse the load received from the spindle 26 rather than the bottom portion 30c2. That is, the surface pressure per unit area can be made smaller in the inclined portion 50 than in the bottom portion 30c2.
- the surface area of the wall portion 30c1 and the surface area of the inclined portion 50 are compared, the surface area of the inclined portion 50 is set smaller, but the wall portion 30c1 is along the axial direction of the through hole 30c.
- a straight portion 40c is provided.
- the straight portion 40c is orthogonal to the direction of rotation of the spindle 26 relative to the hammer 30, and the straight portion 40c functions as a corner where the spindle 26 can come into line contact. That is, when a rolling force is applied to the impact driver 10 and the linear portion 40c and the spindle 26 are in line contact with each other, the surface pressure at the portion increases, and a strong load is generated at the corner portion, thereby causing a galling phenomenon. There is.
- the outer peripheral portion of the spindle 26 is pressed against the inclined portion 50 (the portion having a large contact area). It is desirable to be able to. Therefore, in the present invention, the position of the second pawls 30e1 and 30e2 along the circumferential direction of the hammer 30 and the position of the hammer cams 30a1 and 30a2 along the circumferential direction of the through hole 30c, and the outer peripheral portion of the spindle 26 are inclined portions 50. Is set to a positional relationship in which the hammer 30 and the spindle 26 can come into contact with each other at the inclined portion 50.
- the tops SP of the second claws 30e1 and 30e2 provided on the opposing plane 30d of the hammer 30 are within the range of the inclined part (pressing part) 50 along the circumferential direction of the through hole 30c (within the shaded range in the figure).
- the second claws 30e1 and 30e2 are provided at positions shifted from the wall 30c1 and the bottom 30c2 along the circumferential direction of the hammer 30 so as to enter. That is, when considering the hammer cam 30a1, when the top SP of the second claw 30e1 enters the range of one inclined portion 50 in the circumferential direction of the through hole 30c, the other inclined portion 50 receives the spindle 26. It is configured.
- the inclined portion 50 portion where the spindle 26 hits
- the inclined portion 50 is provided at a position of approximately 90 degrees in the circumferential direction of the through hole 30c from the top SP of the second claw 30e1.
- the top portions SP of the second claws 30e1 and 30e2 are provided on the tip side of the second claws 30e1 and 30e2 that are tapered and in the central portion along the circumferential direction of the hammer 30.
- hammer cams 30a1 and 30a2 formed in the through holes 30c of the hammer 30 are opened (openings OP1 and OP2). is doing.
- the opening shape in the opposing plane 30d of the opening portions OP1 and OP2 of the hammer cams 30a1 and 30a2 is formed in a substantially arc shape in cross section.
- the opening portions (openings OP1 and OP2) of the hammer cams 30a1 and 30a2 are provided with recesses U for making it easy to incorporate the steel balls 29 into the hammer cams 30a1 and 30a2.
- the anvil 18 includes a main body 18c formed in a substantially cylindrical shape.
- a main body 18c formed in a substantially cylindrical shape.
- two first claws 18d1 and 18d2 projecting radially outward are integrally provided. These first claws 18d1 and 18d2 are arranged at intervals of 180 degrees along the circumferential direction of the main body portion 18c, and the cross-sectional shape along the direction intersecting the axis A is substantially rectangular.
- a third contact plane SF3 is provided on one side of the first claws 18d1 and 18d2 along the circumferential direction of the anvil 18.
- a fourth contact plane SF4 is provided on the other side of the first claws 18d1 and 18d2 along the circumferential direction of the anvil 18.
- the second contact plane SF2 of the second claws 30e1 and 30e2 of the hammer 30 is in contact with the third contact plane SF3 over substantially the entire surface.
- the first contact plane SF1 is in contact with substantially the entire surface.
- the width dimension of the first claws 18d1 and 18d2 in the direction outside the radial direction of the anvil 18 and along the circumferential direction is set to about 15 mm. That is, the width is set to be substantially the same as the second claws 30e1 and 30e2 of the hammer 30. As a result, the second claws 30e1 and 30e2 of the hammer 30 can enter between the first claws 18d1 and 18d2 adjacent in the circumferential direction of the anvil 18 with a margin.
- the spindle 26 rotates together with the carrier 25.
- the rotational force of the spindle 26 is transmitted to the hammer 30 via the steel ball 29.
- the rotational force of the hammer 30 is transmitted to the anvil 18 by the engagement of the second claws 30e1 and 30e2 and the first claws 18d1 and 18d2, thereby rotating the anvil 18.
- the rotational force transmitted to the anvil 18 is transmitted to a screw (not shown) via the tip tool 17, and the screw is screwed into an object such as wood.
- the spindle cams 26b1 and 26b2 are formed in a substantially V shape as shown in FIG. 5, and the V-shaped opening side is directed to the speed reducer 21 side (left side in the figure). Accordingly, with the relative rotation of the spindle 26 and the hammer 30, the steel ball 29 rolls toward the speed reducer 21 side of the spindle cams 26b1 and 26b2, and as a result, the hammer 30 resists the spring force of the coil spring 32. Move to 21 side.
- the second claws 30e1 and 30e2 and the first claws 18d1 and 18d2 are disengaged from each other and released from each other, and the rotational force of the hammer 30 is not transmitted to the anvil 18.
- the end of the hammer 30 on the electric motor 12 side collides with the stopper 33, so that the kinetic energy of the hammer 30 is absorbed by the stopper 33. Can be absorbed.
- the steel balls 29 are caused to be hammered by the hammer cams 30a1 and 30a2 by the force of pressing the hammer 30 of the coil spring 32.
- the hammer 30 is moved so as to be close to the anvil 18 while rotating relative to the anvil 18 by rolling inside the spindle cams 26b1 and 26b2.
- the second claws 30e1 and 30e2 of the rotating hammer 30 collide with the first claws 18d1 and 18d2 of the stopped anvil 18, and an impact force is applied in the rotation direction of the anvil 18 and the tip tool 17.
- the screw can be tightened.
- the rotation direction of the electric motor 12 is reversed by operating the forward / reverse switching lever 16, an impact force can be applied in the direction opposite to the above-described operation. Thereby, the tightened screw can be loosened.
- the impact driver 10 when the hammer 30 applies a striking force to the anvil 18, that is, when the striking mechanism SM is operating, if the rotation axis of the impact driver 10 does not coincide with the rotation axis of the screw, the impact driver A turning force acts on the 10 rotation shafts. Then, as shown in FIG. 6 (a), the axis HC of the hammer 30 and the axis SC of the spindle 26 are shifted, and only the first contact plane SF1 of the second claw 30e2 is the fourth contact of the first claw 18d2.
- the impact force F1 is generated by colliding (per one side) with the plane SF4.
- the striking force F1 and the reaction force F2 act at a position shifted by approximately 90 degrees in the circumferential direction of the through hole 30c.
- a rolling force may act on the rotating shaft of the impact driver 10 as shown in FIG.
- the first contact plane SF1 of the second claw 30e1 collides (per part) with the fourth contact plane SF4 of the first claw 18d1, and the striking force F1 is generated.
- the first contact plane SF1 of the second claw 30e2 and the fourth contact plane SF4 of the first claw 18d2 do not collide.
- a reaction force F2 acting in the opposite direction of the striking force F1 acts on the spindle 26, and the spindle 26 is located between the wall 30c1 and the bottom 30c2 along the circumferential direction of the through hole 30c on the hammer cam 30a1 side. It is strongly pressed against the inclined portion (pressing portion) 50 (see the shaded portion in FIG. 4B).
- the dimension along the axial direction of the through hole 30c is smaller than the wall part 30c1
- the dimension along the axial direction of the through hole 30c is smaller than the bottom part 30c2 between the bottom part 30c2 provided at the central part of the hammer cams 30a1 and 30a2 along
- a large inclined portion 50 is provided on which the spindle 26 is pressed when the first claw 18d1 (18d2) and the second claw 30e1 (30e2) are engaged.
- the positions of the second claws 30 e 1 and 30 e 2 along the circumferential direction of the hammer 30 are arranged in the region of the other inclined portion 50 so that the spindle 26 contacts one inclined portion 50 of one hammer cam.
- the second claw is arranged in the region of one inclined portion 50, and the contact portion (the other inclined portion) of the spindle 26 is arranged at a position of about 90 degrees in the circumferential direction of the hammer 30 from the top portion SP of the second claw. .
- the spindle 26 may be pressed against the bottom 30c2 having the smallest surface area (contact area) or the wall 30c1 including the straight portion 40c that functions as a corner. Therefore, it is possible to suppress the caulking phenomenon between the hammer 30 and the spindle 26 and realize the stable operation of the impact driver 10 over a long period of time.
- Embodiment 2 of the present invention will be described in detail with reference to the drawings. Note that portions having the same functions as those in the first embodiment described above are denoted by the same reference numerals, and detailed description thereof is omitted.
- FIG. 7 is a view corresponding to FIG. 3 showing the striking mechanism of the second embodiment
- FIGS. 8A, 8B, and 8C are operation explanatory views of the striking mechanism of FIG. 7 viewed from the axial direction. Show.
- the second embodiment is different from the first embodiment only in the structure of the striking mechanism SM.
- the hammer (striking member) 130 of the striking mechanism SM of the second embodiment is provided with three second claws 130e1, 130e2, 130e3. These second claws 130e1, 130e2, and 130e3 are arranged at intervals of 120 degrees along the circumferential direction of the opposing plane 30d, and the cross-sectional shape along the direction intersecting the axis A is substantially fan-shaped as in the first embodiment. It has become.
- a first contact plane SF1 is provided on one side of the second claws 130e1, 130e2, 130e3 along the circumferential direction of the hammer 130.
- a second contact plane SF2 is provided on the other side of the second claws 130e1, 130e2, 130e3 along the circumferential direction of the hammer 130.
- a first contact plane SF1 is in contact with a fourth contact plane SF4 of first claws 118d1, 118d2, and 118d3 of an anvil (output member) 118, which will be described later, and an anvil 118 is in contact with the second contact plane SF2.
- the third contact plane SF3 of the first claws 118d1, 118d2 and 118d3 is in contact with the substantially entire surface.
- the width dimension of the second claws 130e1, 130e2, and 130e3 in the direction along the circumferential direction in the radial direction outside of the hammer 130 is set to about 10 mm. Accordingly, the first claws 118d1, 118d2, and 118d3 of the anvil 118 can enter with sufficient margin between the second claws 130e1, 130e2, and 130e3 adjacent in the circumferential direction of the hammer 130.
- first claws 118d1, 118d2, and 118d3 projecting radially outward are integrally provided on the hammer 130 side along the axial direction of the main body portion 18c of the anvil 118.
- the first claws 118d1, 118d2, and 118d3 are arranged at intervals of 120 degrees along the circumferential direction of the main body portion 18c, and the cross-sectional shape along the direction intersecting the axis A is substantially rectangular.
- a third contact plane SF3 is provided on one side of the first claws 118d1, 118d2, and 118d3 along the circumferential direction of the anvil 118. Further, a fourth contact plane SF4 is provided on the other side of the first claws 118d1, 118d2, and 118d3 along the circumferential direction of the anvil 118.
- the second contact plane SF2 of the second claws 130e1, 130e2 and 130e3 of the hammer 130 is brought into contact with the third contact plane SF3 on the substantially entire surface, and the second contact plane SF4 of the hammer 130 is placed on the fourth contact plane SF4.
- the first contact plane SF1 of 130e2 and 130e3 is in contact with substantially the entire surface.
- the width dimension of the first claws 118d1, 118d2, and 118d3 in the direction along the radial direction outside the anvil 118 is set to about 10 mm. That is, it is set to have substantially the same width as the second claws 130e1, 130e2, 130e3 of the hammer 130. Accordingly, the second claws 130e1, 130e2, and 130e3 of the hammer 130 can enter with sufficient margin between the first claws 118d1, 118d2, and 118d3 adjacent in the circumferential direction of the anvil 118.
- the positions of the two hammer cams 30a1 and 30a2 provided on the hammer 130 and the positions of the three second claws 130e1, 130e2 and 130e3 provided on the hammer 130 are set to have the following positional relationship. . That is, of the three second claws 130e1, 130e2, and 130e3, the two second claws 130e1 and 130e3 are displaced from the wall 30c1 and the bottom 30c2 (see FIG. 4B) along the circumferential direction of the hammer 130. Is provided. That is, the top portions SP of the second claws 130e1 and 130e3 are within the range of the inclined portion 50 along the circumferential direction of the through hole 30c (see the shaded portion in FIG. 4B). On the other hand, one second claw 130e2 of the three second claws 130e1, 130e2, and 130e3 is provided at a position where the wall portion 30c1 along the circumferential direction of the hammer 130 is located.
- a gap S7 is formed between the second claw 130e3 and the first claw 118d3.
- a reaction force F2 acting in the direction opposite to the striking force F1 acts on the spindle 26, and the spindle 26 is located between the wall portion 30c1 and the bottom portion 30c2 along the circumferential direction of the through hole 30c on the hammer cam 30a2 side. It is strongly pressed against the inclined portion 50 (see the shaded portion in FIG. 4B).
- FIG. 8B shows that the axis HC of the hammer 130 and the axis SC of the spindle 26 are displaced, and only the first contact plane SF1 of the second claw 130e2 collides with the fourth contact plane SF4 of the first claw 118d2 ( This shows a case where the impact force F1 is generated.
- the axis HC of the hammer 130 and the axis SC of the spindle 26 there is a gap S8 between the hammer 130 and the spindle 26, and between the second claw 130e3 and the first claw 118d3.
- a gap S10 is formed between the second claw 130e1 and the first claw 118d1.
- this pattern is one of the three patterns of FIGS. 8A, 8B, and 8C.
- the two patterns are configured to be pressed against the inclined portion 50. Therefore, the galling phenomenon can be sufficiently suppressed as compared with the prior art.
- FIG. 8C shows that the axis HC of the hammer 130 and the axis SC of the spindle 26 are displaced, and only the first contact plane SF1 of the second claw 130e3 collides with the fourth contact plane SF4 of the first claw 118d3 ( This shows a case where the impact force F1 is generated.
- the axis HC of the hammer 130 and the axis SC of the spindle 26 there is a gap S11 between the hammer 130 and the spindle 26, and between the second claw 130e1 and the first claw 118d1.
- a gap S13 is formed between the second claw 130e2 and the first claw 118d2 as the gap S12.
- a reaction force F2 acting in the direction opposite to the striking force F1 acts on the spindle 26, and the spindle 26 is located between the wall portion 30c1 and the bottom portion 30c2 along the circumferential direction of the through hole 30c on the hammer cam 30a2 side. It is strongly pressed against the inclined portion 50 (see the shaded portion in FIG. 4B).
- the same operational effects as those of the first embodiment described above can be obtained.
- three each of the first claw and the second claw are provided, so that the hitting efficiency can be improved, and the working time can be shortened. .
- FIGS. 9A, 9B, and 9C are operation explanatory views of the striking mechanism of the third embodiment as viewed from the axial direction.
- the positions of the two hammer cams 30a1 and 30a2 provided on the hammer (striking member) 230 and the three first positions provided on the hammer 230 are compared to the second embodiment.
- the relationship with the positions of the two claws 130e1, 130e2, 130e3 is slightly different. Specifically, all of the three second claws 130e1, 130e2, and 130e3 are provided at positions shifted from the wall portion 30c1 and the bottom portion 30c2 (see FIG. 4) along the circumferential direction of the hammer 230, respectively.
- FIGS. 9A, 9B, and 9C there are three patterns shown in FIGS. 9A, 9B, and 9C in which the spindle 26 is pressed against the hammer 230.
- FIG. two patterns shown in FIGS. 9 (a) and 9 (b) indicate that the spindle 26 has an inclined portion 50 (of FIG. 4 (b)) between the wall portion 30c1 and the bottom portion 30c2 along the circumferential direction of the through hole 30c. Each pattern is strongly pressed against the shaded area.
- the pattern shown in FIG. 9C is a pattern in which the spindle 26 is strongly pressed against the wall 30c1 (see FIG. 4B) between the hammer cams 30a1 and 30a2 along the circumferential direction of the through hole 30c. Yes.
- FIG. 9C only the pattern shown in FIG. 9C is an unfavorable pattern. Two of the three patterns (a), (b), and (c) are pressed against the inclined portion 50.
- FIG. 10 is a diagram corresponding to FIG. 4 (b) showing a development view of the through hole of the hammer
- FIGS. 11 (a) and 11 (b) are axes of a hammering mechanism in which the hammer of FIG. 10 is applied to the hammering mechanism of FIG. The operation
- movement explanatory drawing seen from the direction is each shown.
- the hammer 30 shown in FIG. 10 is different from FIG. 4B in that the positions of the second claws 30e1 and 30e2 with respect to the central portion CP of the two hammer cams 30a1 and 30a2 and the addition of the steel balls 29 are different.
- the structure and function are the same as those in FIG. Specifically, as shown in FIG. 10, the second claws 30e1 and 30e2 of the hammer 30 are located on the right side in the figure with respect to the central portion CP.
- steel balls 29 are arranged on the arc portions 40a of the two hammer cams 30a1 and 30a2. In FIG. 4B, the steel ball 29 is omitted.
- the anvil 18 includes a main body 18c formed in a substantially cylindrical shape.
- an overlapping portion 18e formed in a substantially disc shape is integrally provided on the hammer 30 side along the axial direction of the main body portion 18c.
- a diameter d1 of the overlapping portion 18e is set to be slightly smaller than a distance d2 (see FIG. 11A) connecting the radially outer sides of the pair of openings OP1 and OP2 (d1 ⁇ d2).
- the overlapping portion 18e is integrally provided with two first claws 18d1 and 18d2 so as to face each other with the main body portion 18c as a center.
- the first claws 18d1 and 18d2 are provided so as to project outward in the radial direction of the overlapping portion 18e, and are arranged at intervals of 180 degrees along the circumferential direction of the overlapping portion 18e.
- the cross-sectional shape along the direction intersecting the axis A of the first claws 18d1 and 18d2 is substantially rectangular.
- an alternate long and short dash line is shown at the boundary between the overlapping portion 18e and the first claws 18d1 and 18d2.
- the first claw 18d1, 18d2 and the second claw 30e1, 30e2 are engaged (contacted) during forward rotation, and the first claw is viewed from the axial direction of the spindle 26.
- the claws 18d1 and 18d2 are located at positions where they overlap the central portions CP of the hammer cams 30a1 and 30a2. That is, the overlapping portion 18e not only overlaps with more than half of the openings OP1 and OP2 when viewed from the axial direction of the spindle 26, but also covers the openings OP1 and OP2 by the first claws 18d1 and 18d2.
- first claws 18 d 1 and 18 d 2 also overlap with the steel balls 29 when viewed from the axial direction of the spindle 26.
- the opening area S1 of each opening part OP1, OP2 can be made still smaller, the grease leak from opening part OP1, OP2 can be suppressed, and the steel ball 29 has opening parts OP1, OP2. It is also possible to suppress falling off from.
- the steel balls 29 push out the grease accumulated in the bottom portions 30c2 of the hammer cams 30a1 and 30a2 to the OP1 and OP2, and the grease adhered to the steel balls 29 reaches the openings OP1 and OP2 of the hammer cams 30a1 and 30a2. After that, it tries to leak out of the hammer 30.
- the first claws 18d1 and 18d2 are connected to the spindle while the first claws 18d1 and 18d2 are engaged with the second claws 30e1 and 30e2. It overlaps with the steel ball 29 as seen from the axial direction of 26 (anvil 18). Furthermore, it overlaps with the central part CP (the top part of the bottom part 30c2 of the hammer cams 30a1 and 30a2) of the hammer cams 30a1 and 30a2.
- the first claws 18d1 and 18d2 do not overlap the steel ball 29 from the axial direction of the spindle 26, but more than half of the openings OP1 and OP2 are overlapped with the overlapping portion 18e. overlapping. Therefore, leakage of the grease adhering to the steel ball 29 to the outside of the hammer 30 can be suppressed in substantially the same way as during “forward rotation” when performing a screw tightening operation or the like.
- the portion covering the openings OP1 and OP2 is smaller than in the case of “forward rotation” when performing screw tightening operation or the like. That is, the opening area S2 is slightly increased (S2> S1).
- the hitting operation during the screw loosening operation is much less than the hitting operation during the screw tightening operation or the like. Therefore, the difference in the opening area of the openings OP1 and OP2 that occurs between “forward rotation” and “reverse rotation” hardly poses a problem in the present embodiment.
- the overlapping portion 18e that overlaps the openings OP1 and OP2 of the hammer cams 30a1 and 30a2 from the axial direction of the spindle 26 is provided on the hammer 30 side of the anvil 18. Since the first claw 18d1, 18d2 and the second claw 30e1, 30e2 engage with each other and perform a striking operation, leakage of the grease attached to the steel ball 29 to the outside can be suppressed. Thereby, the long-term stable operation of the impact driver 10 can be realized.
- the first claws 18d1 and 18d2 and the second claws 30e1 and 30e2 are engaged at the time of “forward rotation” when performing a screw tightening operation or the like.
- the first claws 18d1 and 18d2 overlap with the central portion CP of the hammer cams 30a1 and 30a2 when viewed from the axial direction of the spindle 26, in other words, overlap with the steel balls 29. Therefore, in the “screw tightening operation” that is most frequently used as the impact driver 10, it is effective that the grease adhering to the steel ball 29 leaks out of the hammer 30 from the openings OP1 and OP2 of the hammer cams 30a1 and 30a2. Can be suppressed. Further, the drop of the steel ball 29 from the openings OP1 and OP2 can be further suppressed.
- FIG. 12 (a) and 12 (b) show a corresponding view of FIG. 11 showing the striking mechanism of the fifth embodiment.
- the fifth embodiment differs from the first embodiment only in the structure of the hammer (striking member) 130 and the anvil (output member) 118 that form the striking mechanism SM.
- the diameter dimension d3 of the overlapping part 118a provided in the anvil 118 is set to be slightly larger than the distance d2 connecting the radially outer sides of the pair of openings OP1 and OP2 (d3> d2).
- the radial dimension (projecting dimension outward from the overlapping portion 118a) t of the second claws 130e1 and 130e2 provided on the hammer 130 is set to the fourth embodiment. It is thinner than (see FIG. 11). That is, in the second embodiment, the overlapping portion 118a overlaps the entire opening portions OP1 and OP2 from the axial direction of the spindle 26 (anvil 118).
- the fifth embodiment formed as described above it is possible to achieve substantially the same operational effects as in the fourth embodiment described above.
- the fifth embodiment since the overlapping portion 118a overlaps the entire opening portions OP1 and OP2, leakage of the grease attached to the steel balls 29 to the outside can be more reliably suppressed.
- the overlapping portion 118a of the fifth embodiment is larger (heavy) than the overlapping portion 18e of the fourth embodiment, the rise to the target rotational speed of the electric motor 12 when the electric motor 12 is started up. The speed will be slow.
- the inertia since the inertia is large, it can continue to rotate with the inertial force even after the electric motor 12 is stopped, and as a result, the same level of screw tightening as in the fourth embodiment can be performed.
- FIG. 13 is an exploded perspective view of the striking mechanism of the sixth embodiment, and FIGS. 14A and 14B are operation explanatory views of the striking mechanism of FIG. 13 viewed from the axial direction.
- the striking mechanism of FIG. 13 has the same function (structure) as the striking mechanism of FIG. 7, but for convenience, different symbols are attached to the hammer.
- the sixth embodiment differs from the fourth embodiment only in the structure of the hammer (striking member) 230 and the anvil (output member) 218 that form the striking mechanism SM. ing.
- the hammer 230 is provided with three second claws 230e1, 230e2, and 230e3. These second claws 230e1, 230e2, 230e3 are arranged at intervals of 120 degrees along the circumferential direction of the opposing plane 30d.
- a first contact plane SF1 is provided on one side of the second claws 230e1, 230e2, 230e3 along the circumferential direction of the hammer 230.
- a second contact plane SF2 is provided on the other side of the second claws 230e1, 230e2, 230e3 along the circumferential direction of the hammer 230.
- the first contact plane SF1 is in contact with the fourth contact plane SF4 of the first claws 218d1, 218d2, and 218d3 of the anvil 218 over substantially the entire surface
- the second contact plane SF2 is in contact with the first claws 218d1 of the anvil 218.
- the third contact plane SF3 of 218d2 and 218d3 is in contact with substantially the entire surface.
- the width dimension of the second claws 230e1, 230e2, 230e3 in the direction along the circumferential direction and outside the hammer 230 is set to about 10 mm.
- the first claws 218d1, 218d2, and 218d3 of the anvil 218 can enter between the second claws 230e1, 230e2, and 230e3 adjacent in the circumferential direction of the hammer 230 with a margin.
- the overlapping portion 18e of the anvil 218 is integrally provided with three first claws 218d1, 218d2, and 218d3 protruding outward in the radial direction.
- the first claws 218d1, 218d2, and 218d3 are arranged at intervals of 120 degrees along the circumferential direction of the overlapping portion 18e.
- a third contact plane SF3 is provided on one side of the first claws 218d1, 218d2, 218d3 along the circumferential direction of the anvil 218. Further, a fourth contact plane SF4 is provided on the other side of the first claws 218d1, 218d2, 218d3 along the circumferential direction of the anvil 218.
- the second contact planes SF2 of the second claws 230e1, 230e2, 230e3 of the hammer 230 are in contact with the third contact plane SF3 substantially on the entire surface, and the second claws 230e1, of the hammer 230 are in contact with the fourth contact plane SF4.
- the first contact plane SF1 of 230e2 and 230e3 is in contact with substantially the entire surface.
- the width dimension of the first claws 218d1, 218d2, 218d3 in the direction along the radial direction outside the anvil 218 is set to about 10 mm. That is, the width dimension is set to be substantially the same as that of the second claws 230e1, 230e2, 230e3 of the hammer 230. Accordingly, the second claws 230e1, 230e2, and 230e3 of the hammer 230 can enter with sufficient margin between the first claws 218d1, 218d2, and 218d3 adjacent in the circumferential direction of the anvil 218.
- the positions of the two hammer cams 30a1 and 30a2 provided on the hammer 230 and the positions of the three second claws 230e1, 230e2 and 230e3 provided on the hammer 230 are set in a positional relationship as shown below. . That is, of the three second claws 230e1, 230e2, 230e3, the two second claws 230e1, 230e3 are provided at positions shifted from the wall portion 30c1 and the bottom portion 30c2 (see FIG. 10) along the circumferential direction of the hammer 230. ing.
- the top portions SP of the second claws 230e1 and 230e3 are within the range of the inclined portion 50 along the circumferential direction of the through hole 30c (see FIG. 10).
- one second claw 230e2 of the three second claws 230e1, 230e2, 230e3 is provided at a position where the wall portion 30c1 along the circumferential direction of the hammer 130 is located.
- the first claws 218d1, 218d2, 218d3 and the second claws 230e1, 230e2, 230e3 are engaged at the time of “forward rotation” when performing screw tightening work or the like.
- the first claw 218d1 overlaps the steel ball 29 from the axial direction of the spindle 26 (anvil 218).
- the grease adhering to the steel ball 29 is prevented from leaking out of the hammer 230 from the opening OP1 of the hammer cam 30a1.
- the total opening area (shaded portion in the figure) of the openings OP1 and OP2 at this time is S3.
- the first claw 218d2 is in a state where the first claw 218d1, 218d2, 218d3 and the second claw 230e1, 230e2, 230e3 are engaged. Is overlapped with the steel ball 29 from the axial direction of the spindle 26. Thereby, it is suppressed that the grease adhering to the steel ball 29 leaks out of the hammer 230 from the opening OP2 of the hammer cam 30a2.
- the total opening area of the openings OP1 and OP2 at this time is also S3 as in the case of “forward rotation”.
- the openings OP1 and OP2 are used for “forward rotation” when performing screw tightening work or the like and during “reverse rotation” when performing screw loosening work or the like. Can be made the same S3. Therefore, the leakage of the grease adhering to the steel ball 29 to the outside can be effectively suppressed regardless of “forward rotation” and “reverse rotation”.
- three first claws and three second claws are provided, so that the hitting efficiency can be improved, and the working time can be shortened.
- FIGS. 15A and 15B are diagrams corresponding to FIG. 11 showing the striking mechanism of the seventh embodiment.
- the seventh embodiment is different from the sixth embodiment only in the structures of the hammer (striking member) 330 and the anvil (output member) 318 that form the striking mechanism SM.
- the diameter d4 of the overlapping portion 318a provided in the anvil 318 is set to be slightly larger than the distance d2 connecting the radially outer sides of the pair of openings OP1 and OP2 (d4> d2).
- the radial dimension (thickness dimension) T of the second claws 330e1, 330e2, and 330e3 provided on the hammer 330 is compared with that of the sixth embodiment (see FIG. 14).
- the overlapping portion 318a overlaps the entire opening portions OP1 and OP2 from the axial direction of the spindle 26 (anvil 318).
- the seventh embodiment formed as described above it is possible to achieve substantially the same operational effects as in the sixth embodiment described above.
- the seventh embodiment since the overlapping portion 318a overlaps with the entire opening portions OP1 and OP2, leakage of the grease adhering to the steel ball 29 to the outside can be more reliably suppressed.
- the impact tool of the present invention includes an impact wrench and the like in addition to the impact driver 10 described above.
- the impact tool of the present invention includes a structure that can supply electric power from an AC power source to the electric motor 12 without using the battery pack 11.
- the impact tool of the present invention includes a structure capable of switching the power of the battery pack 11 and the power of the AC power source and supplying the power to the electric motor 12.
- the drive source of the present invention includes an engine, a pneumatic motor, a hydraulic motor, and the like in addition to the electric motor 12 described above.
- the engine is a power source that converts thermal energy generated by burning fuel into kinetic energy, and includes, for example, a gasoline engine, a diesel engine, and a liquefied petroleum gas engine.
- the electric motor 12 includes a brushed motor, a brushless motor, and the like.
- the impact tool of the present invention includes a structure in which the tip tool is attached to the anvil via a socket, an adapter, or the like.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Portable Power Tools In General (AREA)
- Percussive Tools And Related Accessories (AREA)
Abstract
Description
Claims (11)
- 先端工具に回転力および打撃力を与える打撃工具であって、
モータと、前記モータにより回転されるスピンドルと、
前記先端工具が取り付けられるアンビルと、
前記スピンドルの回転力を前記アンビルの回転力および打撃力に変換するハンマと、を備え、
前記ハンマは、前記アンビルの第1爪と係合する第2爪と、前記スピンドルが貫通する貫通孔と、前記貫通孔の径方向外側に窪んだ複数のカム溝と、前記貫通孔の周方向において前記複数のカム溝の間に設けられた壁部と、前記貫通孔の周方向において前記カム溝の中央部に位置する底部と、を有し、
前記貫通孔の周方向において、前記第2爪は前記底部と前記壁部との間に設けられる、打撃工具。 - 径方向内側において周方向の中央部分に設けられた前記第2爪の頂部が前記底部と前記壁部との間に位置する、請求項1に記載の打撃工具。
- 前記第2爪は複数設けられ、前記複数の第2爪のうちの少なくとも1つが前記底部と前記壁部との間に設けられる、請求項1に記載の打撃工具。
- 前記第1爪および前記第2爪を3つずつ設けた、請求項3に記載の打撃工具。
- 先端工具に回転力および打撃力を与える打撃工具であって、
モータと、
前記モータにより回転されるスピンドルと、
前記先端工具が取り付けられるアンビルと、
前記スピンドルの回転力を前記アンビルの回転力および打撃力に変換するハンマと、を備え、
前記ハンマは、前記アンビルの第1爪と係合する第2爪と、前記スピンドルが貫通する貫通孔と、前記貫通孔の径方向外側に窪んだ一対のカム溝と、前記貫通孔の周方向において前記一対のカム溝の間に設けられた壁部と、前記貫通孔の周方向において前記一対のカム溝の夫々の中央部に位置する底部と、前記貫通孔の周方向において前記壁部と前記底部との間に位置しそれらを繋ぐ傾斜部と、を有し、
前記貫通孔の周方向において前記壁部、前記傾斜部、前記底部、前記傾斜部、前記壁部が並んで設けられて前記カム溝を形成し、
前記第2爪の周方向における中央部が一方の前記傾斜部の領域内に位置すると共に、前記第1爪と前記第2爪とが係合したときに他方の前記傾斜部に前記スピンドルが押し付けられるように構成した、打撃工具。 - 前記第2爪は複数設けられ、前記複数の第2爪のうちの少なくとも1つの周方向における中央部が一方の前記傾斜部の領域内に位置すると共に、前記第1爪と前記第2爪とが係合したときに他方の前記傾斜部に前記スピンドルが押し付けられるように構成した、請求項5に記載の打撃工具。
- 前記第1爪および前記第2爪を3つずつ設けた、請求項6に記載の打撃工具。
- 先端工具に回転力および打撃力を与える打撃工具であって、
モータと、
前記モータにより回転されるスピンドルと、
第1爪を有し、前方側に前記先端工具が取り付けられるアンビルと、
前記アンビルの後方側に設けられ、前記第1爪と係合する第2爪と、前方側が開口し後方側に底部を有し前記スピンドルと共に鋼球を保持するカム溝と、を有し、前記スピンドルの回転力を前記アンビルの回転力および打撃力に変換するハンマと、を備え、
前記第1爪と前記第2爪とが係合した状態のもとで、前記スピンドルの軸方向から見て前記第1爪が前記カム溝の前記底部と重なるように構成した、打撃工具。 - 前記第1爪が複数設けられ、前記複数の第1爪のうちの少なくとも1つが前記底部と重なる、請求項8に記載の打撃工具。
- 前記第1爪と前記第2爪とが係合した状態のもとで、前記第1爪が前記回転部材の軸方向から見て前記鋼球と重なる、請求項8に記載の打撃工具。
- 前記第1爪および前記第2爪を3つずつ設けた、請求項10に記載の打撃工具。
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP15827439.9A EP3175954B1 (en) | 2014-07-31 | 2015-07-24 | Impact tool |
US15/500,244 US20170259412A1 (en) | 2014-07-31 | 2015-07-24 | Impact tool |
CN201580040804.7A CN106573364B (zh) | 2014-07-31 | 2015-07-24 | 冲击工具 |
JP2016538321A JP6341283B2 (ja) | 2014-07-31 | 2015-07-24 | 打撃工具 |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2014157223 | 2014-07-31 | ||
JP2014-157223 | 2014-07-31 | ||
JP2014-157216 | 2014-07-31 | ||
JP2014157216 | 2014-07-31 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2016017545A1 true WO2016017545A1 (ja) | 2016-02-04 |
Family
ID=55217446
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2015/071124 WO2016017545A1 (ja) | 2014-07-31 | 2015-07-24 | 打撃工具 |
Country Status (5)
Country | Link |
---|---|
US (1) | US20170259412A1 (ja) |
EP (1) | EP3175954B1 (ja) |
JP (1) | JP6341283B2 (ja) |
CN (1) | CN106573364B (ja) |
WO (1) | WO2016017545A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR101877811B1 (ko) * | 2017-04-10 | 2018-07-13 | (주)중우엠텍 | 슬라이드식 핀해머가 구비된 회전력 전달장치 |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN107355528A (zh) * | 2016-05-10 | 2017-11-17 | 德昌电机(深圳)有限公司 | 一种驱动装置及应用该驱动装置的电动工具 |
DE102017122862B4 (de) * | 2017-10-02 | 2023-03-16 | C. & E. Fein Gmbh | Schlagschrauber |
CN211805946U (zh) | 2018-07-18 | 2020-10-30 | 米沃奇电动工具公司 | 动力工具 |
US11705778B2 (en) | 2019-12-19 | 2023-07-18 | Black & Decker Inc. | Power tool with compact motor assembly |
US11509193B2 (en) | 2019-12-19 | 2022-11-22 | Black & Decker Inc. | Power tool with compact motor assembly |
US11980948B2 (en) * | 2019-12-26 | 2024-05-14 | Koki Holdings Co., Ltd. | Rotary tool |
EP4171881A1 (en) * | 2020-06-29 | 2023-05-03 | Gérard Grand | Impact mechanism for rotary tool |
WO2022067235A1 (en) * | 2020-09-28 | 2022-03-31 | Milwaukee Electric Tool Corporation | Impulse driver |
JP2022106194A (ja) * | 2021-01-06 | 2022-07-19 | 株式会社マキタ | インパクト工具 |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH01170570U (ja) * | 1988-05-20 | 1989-12-01 | ||
JP2001219383A (ja) * | 2000-02-04 | 2001-08-14 | Makita Corp | 回転打撃工具 |
JP2003220569A (ja) * | 2002-01-28 | 2003-08-05 | Matsushita Electric Works Ltd | インパクト回転工具 |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3208569A (en) * | 1963-01-16 | 1965-09-28 | Adee Clarice Berry | Impact clutch with sliding key in anvil |
CN201046559Y (zh) * | 2007-04-23 | 2008-04-16 | 镁迪企业股份有限公司 | 动力工具打击结构 |
AU2009244202B2 (en) * | 2008-05-07 | 2014-09-11 | Milwaukee Electric Tool Corporation | Drive assembly for a power tool |
EP2140977B1 (de) * | 2008-07-01 | 2012-04-25 | Metabowerke GmbH | Schlagschrauber |
JP4457170B1 (ja) * | 2009-06-03 | 2010-04-28 | 株式会社空研 | インパクトレンチ |
CN201437237U (zh) * | 2009-07-10 | 2010-04-14 | 海峰机械工业股份有限公司 | 旋转冲击工具头 |
US9616558B2 (en) * | 2009-07-29 | 2017-04-11 | Hitachi Koki Co., Ltd. | Impact tool |
DE102010031499A1 (de) * | 2010-07-19 | 2012-01-19 | Robert Bosch Gmbh | Handwerkzeugmaschine mit einem mechanischen Schlagwerk |
JP3164609U (ja) * | 2010-09-27 | 2010-12-09 | 邱 奕宗 | 電動工具に使用する動力モード転換装置 |
DE102011017671A1 (de) * | 2011-04-28 | 2012-10-31 | Hilti Aktiengesellschaft | Handwerkzeugmaschine |
US9272400B2 (en) * | 2012-12-12 | 2016-03-01 | Ingersoll-Rand Company | Torque-limited impact tool |
WO2016121462A1 (ja) * | 2015-01-30 | 2016-08-04 | 日立工機株式会社 | 打撃作業機 |
-
2015
- 2015-07-24 JP JP2016538321A patent/JP6341283B2/ja active Active
- 2015-07-24 CN CN201580040804.7A patent/CN106573364B/zh active Active
- 2015-07-24 EP EP15827439.9A patent/EP3175954B1/en active Active
- 2015-07-24 US US15/500,244 patent/US20170259412A1/en not_active Abandoned
- 2015-07-24 WO PCT/JP2015/071124 patent/WO2016017545A1/ja active Application Filing
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH01170570U (ja) * | 1988-05-20 | 1989-12-01 | ||
JP2001219383A (ja) * | 2000-02-04 | 2001-08-14 | Makita Corp | 回転打撃工具 |
JP2003220569A (ja) * | 2002-01-28 | 2003-08-05 | Matsushita Electric Works Ltd | インパクト回転工具 |
Non-Patent Citations (1)
Title |
---|
See also references of EP3175954A4 * |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR101877811B1 (ko) * | 2017-04-10 | 2018-07-13 | (주)중우엠텍 | 슬라이드식 핀해머가 구비된 회전력 전달장치 |
Also Published As
Publication number | Publication date |
---|---|
US20170259412A1 (en) | 2017-09-14 |
EP3175954A4 (en) | 2018-03-21 |
JPWO2016017545A1 (ja) | 2017-04-27 |
CN106573364A (zh) | 2017-04-19 |
EP3175954B1 (en) | 2020-12-02 |
CN106573364B (zh) | 2020-01-21 |
JP6341283B2 (ja) | 2018-06-13 |
EP3175954A1 (en) | 2017-06-07 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
JP6341283B2 (ja) | 打撃工具 | |
US20050061521A1 (en) | Power tool | |
US10668602B2 (en) | Impact rotary tool | |
JP6832509B2 (ja) | 回転打撃工具 | |
TWI572453B (zh) | 滾珠偏位倒角 | |
JP2012011533A (ja) | 打撃工具 | |
JP2016117140A (ja) | 回転工具 | |
JP2015112682A (ja) | インパクト回転工具 | |
JP2009172732A (ja) | インパクト回転工具 | |
WO2018061389A1 (ja) | 回転打撃工具 | |
WO2014208058A1 (en) | Striking tool | |
JP2013022691A (ja) | インパクト回転工具 | |
WO2018061388A1 (ja) | 回転打撃工具 | |
WO2015182512A1 (ja) | 打撃工具 | |
WO2019167498A1 (ja) | インパクト工具 | |
JP6455227B2 (ja) | 打撃工具 | |
JPWO2015182513A1 (ja) | 打撃工具 | |
JP6217849B2 (ja) | 打撃工具 | |
JP2014188612A (ja) | 打撃工具 | |
WO2018142742A1 (ja) | 回転打撃工具 | |
JP6638856B2 (ja) | ねじ締め工具 | |
JP6719084B2 (ja) | 回転打撃工具 | |
JP6607502B2 (ja) | インパクト回転工具 | |
JP2018051713A (ja) | 電動工具 | |
WO2018159171A1 (ja) | 打撃作業機 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 15827439 Country of ref document: EP Kind code of ref document: A1 |
|
ENP | Entry into the national phase |
Ref document number: 2016538321 Country of ref document: JP Kind code of ref document: A |
|
REEP | Request for entry into the european phase |
Ref document number: 2015827439 Country of ref document: EP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 15500244 Country of ref document: US |
|
NENP | Non-entry into the national phase |
Ref country code: DE |