WO2018061388A1 - Outil à percussion rotative - Google Patents

Outil à percussion rotative Download PDF

Info

Publication number
WO2018061388A1
WO2018061388A1 PCT/JP2017/024811 JP2017024811W WO2018061388A1 WO 2018061388 A1 WO2018061388 A1 WO 2018061388A1 JP 2017024811 W JP2017024811 W JP 2017024811W WO 2018061388 A1 WO2018061388 A1 WO 2018061388A1
Authority
WO
WIPO (PCT)
Prior art keywords
hammer
spindle
main
rotation axis
main hammer
Prior art date
Application number
PCT/JP2017/024811
Other languages
English (en)
Japanese (ja)
Inventor
雅理 村松
隆司 草川
Original Assignee
パナソニックＩｐマネジメント株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by パナソニックＩｐマネジメント株式会社 filed Critical パナソニックＩｐマネジメント株式会社
Publication of WO2018061388A1 publication Critical patent/WO2018061388A1/fr

Links

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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D16/00—Portable percussive machines with superimposed rotation, the rotational movement of the output shaft of a motor being modified to generate axial impacts on the tool bit

Definitions

  • the present invention relates to a rotary impact tool.
  • the hammer In the rotary impact tool, the hammer is urged toward the anvil side by a spring so that the hammer claw and the anvil claw are engaged in the circumferential direction, and the rotation of the hammer is transmitted to the anvil.
  • a load torque exceeding a predetermined value is applied to the anvil, the hammer moves backward against the spring biasing force.
  • the hammer claw and the anvil claw are disengaged due to the retraction of the hammer, the hammer advances while rotating, and the hammer claw strikes the anvil claw in the rotation direction.
  • Patent Document 1 discloses an impact including a spindle rotated by a driving unit, an anvil disposed in front of the spindle in the rotation axis direction, and a rotary striking mechanism that converts the rotation of the spindle into a rotational striking and transmits it to the anvil.
  • the rotary striking mechanism includes a main hammer that can rotate about the rotation axis of the spindle and move in the axial direction, and a sub hammer that rotates integrally with the main hammer but does not move in the axial direction.
  • the magnitude of the impact in the direction of the rotation axis is proportional to the mass of the hammer hitting the anvil, and the magnitude of the impact in the direction of rotation is the moment of inertia of the rotating hammer Proportional to the sum of the product of the distance to the axis and the square.
  • the impact wrench of Patent Document 1 adopts a double hammer configuration, and the mass of the auxiliary hammer that contributes only to the impact in the rotational direction is made larger than the mass of the main hammer, thereby maintaining the magnitude of the impact in the rotational direction.
  • the impact of the hammer in the direction of the rotation axis is reduced.
  • the inventors of the present invention have come up with a technique for reducing the vibration in the rotation axis direction transmitted to the tool body by changing the double hammer configuration disclosed in Patent Document 1.
  • the present invention has been made in view of such circumstances, and an object thereof is to provide a technique for reducing vibration in the rotation axis direction transmitted to the tool body in a rotary impact tool having a main hammer and a sub hammer. is there.
  • a rotary impact tool includes a drive unit, a spindle that is rotated by the drive unit, a main unit that is rotatable about the rotation axis of the spindle and is movable in the direction of the rotation axis.
  • the rotary impact tool of this aspect is configured such that when the main hammer moves in the rotation axis direction, the sub hammer moves in the direction opposite to the movement direction of the main hammer.
  • the rotary impact tool of this aspect includes three or more second cam structures, and the auxiliary hammer is supported by second steel balls included in the three or more second cam structures.
  • FIG. 1 A) is a front side perspective view of a main hammer
  • (b) is a perspective view of a spindle and a carrier
  • (c) is a rear side perspective view of a sub hammer.
  • (A) And (b) is a figure which shows the operation state of a 1st cam structure.
  • (A)-(c) is a figure which shows the positional relationship which expanded the engagement surface of the main hammer and the anvil typically in the circumferential direction.
  • A) And (b) is a figure which shows the operation state of a 2nd cam structure.
  • (A)-(c) is a figure which shows the rotation impact mechanism which concerns on embodiment. It is a schematic sectional drawing of a rotation impact mechanism.
  • the rotary impact tool of the embodiment includes a spindle rotated by a drive unit, an anvil disposed in front of the spindle in the rotation axis direction, and a rotary impact mechanism that converts rotation of the spindle into rotational impact and transmits the rotational impact to the anvil.
  • the rotary hammering mechanism employs a double hammer configuration, and includes a main hammer that is rotatable about the rotation axis of the spindle and is movable in the axial direction, and a sub hammer that is rotatable integrally with the main hammer.
  • the rotary striking mechanism has a function of causing the main hammer to impactably engage the anvil and rotating the anvil about the axis.
  • FIG. 1 is a schematic cross-sectional view of a main part of a rotary impact tool according to an embodiment.
  • an alternate long and short dash line indicates a rotation axis of the rotary impact tool 1.
  • FIG. 2 is an exploded perspective view of components of the rotary impact mechanism according to the embodiment
  • FIG. 3 is an assembled perspective view of the rotary impact mechanism according to the embodiment.
  • the illustration of a later-described stopper member 27 is omitted for ease of viewing.
  • 4A is a front perspective view of the main hammer
  • FIG. 4B is a perspective view of the spindle and the carrier
  • FIG. 4C is a rear perspective view of the auxiliary hammer.
  • the rotary impact tool 1 includes a housing 2 that constitutes a tool body.
  • the upper part of the housing 2 forms an accommodation space for accommodating various components, and the lower part of the housing 2 constitutes a grip portion 3 that is gripped by the user.
  • An operation switch 4 that is operated by a user's finger is provided on the front side of the grip 3, and a battery (not shown) that supplies power to the drive unit 10 is provided at the lower end of the grip 3.
  • the drive unit 10 is an electric motor, and the drive shaft 10 a of the drive unit 10 is connected to the carrier 16 and the spindle 11 via the power transmission mechanism 12.
  • the carrier 16 is located on the rear end side of the spindle 11 and accommodates a power transmission gear.
  • the carrier 16 is configured as a large-diameter portion having an outer diameter larger than that of the spindle 11.
  • the carrier 16 has a front member 16b having a diameter larger than that of the spindle 11, and a rear member 16c positioned rearward of the front member 16b, and accommodates a gear between the front member 16b and the rear member 16c.
  • the space 16d is formed.
  • the power transmission mechanism 12 includes a sun gear 13 that is press-fitted and fixed to the tip of the drive shaft 10 a, two planetary gears 14 that mesh with the sun gear 13, and an internal gear 15 that meshes with the planetary gear 14.
  • the planetary gear 14 is rotatably supported in a space 16d of the carrier 16 by a support shaft 14a fixed to the front member 16b and the rear member 16c.
  • the internal gear 15 is fixed to the inner peripheral surface of the housing 2.
  • the rotation of the drive shaft 10a is decelerated based on the ratio between the number of teeth of the sun gear 13 and the number of teeth of the internal gear 15, and the rotational torque is increased. .
  • the carrier 16 and the spindle 11 can be driven at low speed and high torque.
  • Rotating impact mechanism of the rotating impact tool 1 includes a spindle 11, a carrier 16, a main hammer 20, a secondary hammer 21 and a spring member 23.
  • the spindle 11 is formed in a columnar shape, and a small-diameter protrusion 11 a is formed at the tip thereof coaxially with the axis of the spindle 11.
  • the protrusion 11a is inserted in a rotatable state into a hole having a cylindrical inner space formed in the rear part of the anvil 22.
  • a steel main hammer 20 having a substantially disc shape and having a through hole in the center is mounted on the outer periphery of the spindle 11.
  • a pair of hammer claws 20 a projecting toward the anvil 22 are formed on the front surface of the main hammer 20.
  • the main hammer 20 is attached to the spindle 11 so as to be rotatable about the rotation axis of the spindle 11 and to be movable in the direction of the rotation axis of the spindle 11, that is, in the front-rear direction.
  • the main hammer 20 can apply a rotational striking force to the anvil 22.
  • the auxiliary hammer 21 is formed as a steel cylindrical member, and is divided into a front part 21a and a rear part 21b by an annular partition part 21e.
  • the sub hammer 21 accommodates the main hammer 20 in the internal space of the front portion 21a.
  • the auxiliary hammer 21 and the main hammer 20 are provided with an integral rotation mechanism that rotates together.
  • the main hammer 20 includes four first pin grooves 20 d on its outer peripheral surface and having a semicircular cross section and parallel to the rotation axis of the spindle 11.
  • the auxiliary hammer 21 includes four second pin grooves 21 c on the inner peripheral surface of the front portion 21 a and having a semicircular cross section and parallel to the rotation axis of the spindle 11.
  • the four second pin grooves 21 c of the sub hammer 21 are formed at positions corresponding to the four first pin grooves 20 d of the main hammer 20.
  • the first pin grooves 20 d may be formed at an interval of 90 degrees on the outer peripheral surface of the main hammer 20.
  • the second pin grooves 21 c are formed at an interval of 90 degrees on the inner peripheral surface of the sub hammer 21.
  • an engagement pin 26 that is a cylindrical member is disposed in the second pin groove 21c.
  • the engagement pin 26 may be a needle roller.
  • the engaging pin 26 is inserted into the second pin groove 21c from the front end side of the sub hammer 21 and inserted to the groove bottom.
  • a stop member 27 having a function of preventing the engagement pin 26 from being detached is fitted into the annular groove 21d formed on the inner peripheral surface of the sub hammer 21.
  • the four first pin grooves 20d of the main hammer 20 and the four engagement pins 26 are aligned with the four engagement pins 26 attached to the four second pin grooves 21c of the sub hammer 21. Then, the main hammer 20 is inserted into the sub hammer 21. As a result, the main hammer 20 and the sub hammer 21 can be rotated together around the rotation axis of the spindle 11.
  • the main hammer 20 has an annular recess 20c on the rear side.
  • the spring member 23 is interposed between the concave portion 20 c of the main hammer 20 and the annular partition portion 21 e of the sub hammer 21.
  • the main hammer 20 can move in the front-rear direction using the engaging pin 26 as a guide, and can apply a rotational striking force to the anvil 22 by the biasing force of the spring member 23.
  • the spindle 11 includes two first guide grooves 11b on the outer peripheral surface thereof, and the main hammer 20 includes two first engagement grooves 20b on the inner peripheral surface of the through hole.
  • the two first guide grooves 11b have the same shape and are arranged in the circumferential direction, and the two first engagement grooves 20b have the same shape and are arranged in the circumferential direction.
  • a steel ball 19 is disposed between the first guide groove 11b and the first engagement groove 20b.
  • the first guide groove 11b on the spindle 11 side, the first engagement groove 20b on the main hammer 20 side, and the steel ball 19 disposed therebetween constitute a “first cam structure”.
  • the two steel balls 19 support the main hammer 20 in the radial direction so that the main hammer 20 can rotate around the rotation axis of the spindle 11 and move in the direction of the rotation axis.
  • the carrier 16 having a diameter larger than that of the spindle 11 includes three second guide grooves 16a on the outer periphery of the front surface of the front member 16b, and the auxiliary hammer 21 includes three second engagement grooves 21f on the rear surface of the annular partition portion 21e. .
  • the three second guide grooves 16a have the same shape and are arranged in the circumferential direction
  • the three second engagement grooves 21f have the same shape and are arranged in the circumferential direction.
  • a steel ball 17 is disposed between the second guide groove 16a and the second engagement groove 21f.
  • the steel ball 17 is preferably the same steel ball as the steel ball 19 from the viewpoint of manufacturing cost.
  • the steel ball 17 is preferably formed of the same material as the steel ball 19 and has the same size.
  • the second guide groove 16a on the carrier 16 side, the second engagement groove 21f on the sub hammer 21 side, and the steel ball 17 disposed between them constitute a “second cam structure”.
  • the three steel balls 17 support the auxiliary hammer 21 in the direction of the rotation axis so that the auxiliary hammer 21 can rotate around the rotation axis of the spindle 11 and move in the direction of the rotation axis.
  • the first guide groove 11b is formed in a V-shape or a U-shape when viewed from the tip side of the tool. That is, the 1st guide groove 11b has two inclination grooves which incline in the back diagonal direction symmetrically from the foremost part.
  • the first engagement groove 20b is formed in a V-shape or U-shape that is opposite to the tool tip side.
  • the second guide groove 16a is formed in a V shape or a U shape as viewed from the rear end side of the tool. That is, the second guide groove 16a has two inclined grooves that are symmetrically inclined in the front oblique direction from the rearmost part.
  • the second engagement groove 21f is formed in a V-shape or U-shape in the reverse direction when viewed from the tool rear end side.
  • the first guide groove 11b and the second guide groove 16a are formed with inclined grooves extending in different directions in the rotation axis direction.
  • the stopper member 30 is provided between the main hammer 20 and the carrier 16 so that the steel ball 19 in the first cam structure and the steel ball 17 in the second cam structure do not collide with the end portions of the respective inclined grooves.
  • the movement range in the direction of the 20 rotation axis is regulated.
  • the stopper member 30 may be formed of a resin material, for example.
  • the anvil 22 that engages with the main hammer 20 is made of steel, and is rotatably supported by the housing 2 via a steel or brass sliding bearing.
  • the tip of the anvil 22 is provided with a tool mounting portion 22a having a square cross section for mounting a socket body to be mounted on the head of a hexagon bolt or a hexagon nut.
  • a pair of anvil claws that engage with the pair of hammer claws 20a of the main hammer 20 are provided at the rear of the anvil 22.
  • Each of the pair of anvil claws is formed as a columnar member having a sectional fan shape.
  • the anvil claw of the anvil 22 and the hammer claw 20a of the main hammer 20 do not necessarily have to be two, and if the number of the respective claws is equal, three or more at equal intervals in the circumferential direction of the anvil 22 and the main hammer 20 It may be provided.
  • FIG. 5A shows the state of the first cam structure immediately after the start of tightening of the bolts and nuts
  • FIG. 5B shows the state of the first cam structure after a lapse of time from the start of tightening.
  • FIG. 5B is a comparative view for comparison with the initial state of the first cam structure shown in FIG. 5A, and the steel ball 19 moves from the foremost part of the first guide groove 11b toward the groove end. It shows how it moves.
  • the steel ball 19 is shown moving to the vicinity of the groove end portion.
  • the circumferential movable range of the second cam structure is narrower than the first cam structure. For this reason, the steel ball 19 moves with the limit in front of the groove end.
  • FIG. 6A shows an engaged state between the hammer claw 20a of the main hammer 20 and the anvil claw 22b of the anvil 22 immediately after the start of tightening the bolts and nuts.
  • a rotational force A due to the rotation of the driving unit 10 is applied to the main hammer 20 in the direction indicated by the arrow. Further, a forward biasing force B by the spring member 23 is applied to the main hammer 20 in the direction indicated by the arrow.
  • the rotational force of the main hammer 20 is transmitted to the anvil 22 by the circumferential engagement of the hammer claws 20a and the anvil claws 22b.
  • a socket body (not shown) attached to the tool mounting portion 22a rotates, and initial tightening is performed by applying a rotational force to the bolts and nuts. Since the spring member 23 applies the urging force B to the main hammer 20, the steel ball 19 is positioned at the foremost part in the first guide groove 11b as shown in FIG. At this time, the hammer claw 20a and the anvil claw 22b are in an engaged state with the maximum engagement length.
  • the hammer claw 20 a moves along the locus indicated by the arrow G, collides with the anvil claw 22 b, and applies a striking force in the rotation direction to the anvil 22. Thereafter, the hammer claw 20a is moved in the direction opposite to the locus G by the reaction, but finally returns to the state shown in FIG. 6A by the rotational force A and the urging force B. The above operation is repeated at a high speed, and the rotational hammering force by the main hammer 20 is repeatedly applied to the anvil 22.
  • the magnitude of the impact in the rotational direction is proportional to the total moment of inertia of the main hammer 20 and the secondary hammer 21, while the magnitude of the impact in the rotational axis direction.
  • the length is proportional to the mass of the main hammer 20.
  • the rotary impact tool 1 of the embodiment Compared with the rotary impact tool 1 using one hammer having the total mass of the main hammer 20 and the secondary hammer 21, the rotary impact tool 1 of the embodiment has the same impact magnitude in the rotational direction as it is in the rotational axis direction. Reduce the magnitude of impact. By making the mass of the main hammer 20 as small as possible compared with the mass of the sub hammer 21, the impact force generated in the direction of the rotation axis can be further reduced.
  • the moment of inertia is increased by utilizing the fact that the magnitude of the moment of inertia is proportional to the square of the turning radius. That is, by providing the auxiliary hammer 21 having a large mass on the outer peripheral side of the main hammer 20, the moment of inertia of the auxiliary hammer 21 is increased and the impact force in the rotational direction by the double hammer is increased.
  • the sub hammer 21 is moved in the direction opposite to the movement of the main hammer 20 in the rotation axis direction, so that the impact generated in the rotation axis direction by the main hammer 20 is canceled and vibration transmitted to the housing 2 is transmitted. It has a role to further reduce.
  • FIG. 7A shows the state of the second cam structure immediately after the start of tightening of the bolts and nuts
  • FIG. 7B shows the state of the second cam structure after a lapse of time from the start of tightening.
  • FIG.7 (b) shows a mode that the steel ball 17 is moving the 2nd guide groove 16a.
  • the secondary hammer 21 moves in the direction opposite to the moving direction (X direction) of the main hammer 20. That is, when the main hammer 20 moves backward, the auxiliary hammer 21 moves forward.
  • the rotary hammer 1 is moved by the first cam structure and the second cam structure so that when the main hammer 20 moves in the rotation axis direction, the sub hammer 21 moves in the direction opposite to the movement direction of the main hammer 20. It is configured.
  • the sub hammer 21 moves in the direction opposite to the movement direction of the main hammer 20 in synchronization with the movement of the main hammer 20, so that vibration generated by the movement of the main hammer 20 in the axial direction can be absorbed and vibration transmitted to the user's hand. Can be reduced.
  • FIG. 8A shows a front view of the rotary striking mechanism.
  • FIG. 8A shows a state where the two steel balls 19 are positioned at the forefront of the first guide groove 11b.
  • the first engagement groove 20b having a shape opposite to that of the first guide groove 11b has two inclined grooves inclined forward from the rearmost part where the steel ball 19 is disposed.
  • FIG. 8B shows a CC cross-sectional view of the rotary impact mechanism. In FIG. 8B, illustration of the spring member 23, the planetary gear 14 and the like is omitted. In this state, the three steel balls 17 are respectively located at the rearmost part of the second guide groove 16a.
  • FIG. 8C shows a DD sectional view of the rotary striking mechanism.
  • the second guide groove 16a has two inclined grooves inclined forward from the rearmost part where the steel ball 17 is disposed.
  • the secondary hammer 21 and the main hammer 20 are restricted from relative rotation about the axis while allowing the relative movement in the axis direction by the engagement pin 26.
  • the auxiliary hammer 21 is pressed against the carrier 16 by the spring member 23, and the rear surface of the annular partition 21 e is supported by three steel balls 17 disposed on the outer periphery of the front member 16 b of the carrier 16.
  • the steel ball 17 must stably support the rear surface of the annular partition 21e in the direction of the rotation axis so that the secondary hammer 21 and the spindle 11 remain coaxial.
  • the rotary impact tool 1 of the embodiment includes three second cam structures in which the steel balls 17 are arranged between the second guide groove 16a and the second engagement groove 21f, and the three steel balls 17 are sub-hammers.
  • the rear surface of the 21 annular partitioning portions 21e is supported at three points in the rotational axis direction.
  • the auxiliary hammer 21 is supported by the three steel balls 17, thereby effectively suppressing the inclination of the auxiliary hammer 21 with respect to the rotation axis direction. It becomes possible to maintain the coaxiality of the auxiliary hammer 21 and the spindle 11.
  • the steel ball 17 is disposed on the outer periphery of the front surface of the front member 16b having a diameter larger than that of the spindle 11. Since the peripheral speed of the outer periphery of the front member 16b is larger than the outer periphery of the spindle 11, if the auxiliary hammer 21 is supported by the same number (two) of steel balls 17 as the steel balls 19 in the first cam structure, It is conceivable that the wear of the steel ball 17 is more advanced than 19. Therefore, the tool reliability can be improved by increasing the number of steel balls 17 in the second cam structure than the number of steel balls 19 in the first cam structure.
  • the three second cam structures are provided at equal intervals in the circumferential direction.
  • the three steel balls 17 are positioned at an interval of 120 degrees from each other, and can support the auxiliary hammer 21 stably.
  • the number of steel balls 17 may be three or more.
  • the rotary impact tool 1 can suppress wear of the steel balls 17 while ensuring the coaxiality between the auxiliary hammer 21 and the spindle 11. Even when four or more second cam structures are provided, it is preferable that the sub hammer 21 is stably supported by the plurality of steel balls 17 being positioned at equal intervals in the circumferential direction.
  • the circumferential range of motion is narrower in the second cam structure.
  • the second cam structure reaches the movable limit earlier than the first cam structure. Therefore, in the rotary impact tool 1, the first cam structure and the second cam are arranged so that the engagement between the hammer claw 20a and the anvil claw 22b is released before the steel ball 17 moves to the movable limit in the second guide groove 16a. A structure is formed.
  • the rotary impact tool 1 is an electric tool that is used by a user by hand, there is a great demand for reduction in size and weight. If the structure in which three second guide grooves 16a are formed on the outer peripheral surface of the spindle 11 and the three steel balls 17 support the auxiliary hammer 21 in the radial direction is adopted, the strength of the spindle 11 is insufficient. It is necessary to thicken itself. However, increasing the diameter of the spindle 11 is not preferable because it does not meet the demand for reduction in size and weight.
  • the steel ball 17 is made smaller than the steel ball 19 to reduce the amount of lightening by forming the three second guide grooves 16a, thereby preventing the strength of the spindle 11 from being insufficient.
  • the strength of the steel ball 17 becomes a problem this time, and the manufacturing cost increases because two types of steel balls are required.
  • the second guide groove 16 a is formed in the carrier 16 having a diameter larger than that of the spindle 11 to solve the above problem.
  • a large-diameter portion having an outer diameter larger than that portion may be provided on the rear side of the portion where the first guide groove 11b of the spindle 11 is formed, and the second guide groove 16a may be formed in the large-diameter portion.
  • the spindle 11 has a small diameter portion in which the first guide groove 11b is formed and a large diameter portion in which the second guide groove 16a is formed.
  • the weight of the spindle 11 is slightly increased, but at the same time, the strength of the carrier 16 is increased. Therefore, when sufficient durability can be expected, the carrier 16 is thinned (lightened). Thus, the tool weight may not be increased.
  • FIG. 9 is a schematic cross-sectional view of the rotary impact mechanism when the steel ball moves in the first cam structure and the second cam structure.
  • the main hammer 20 moves backward by the movement amount M with respect to the spindle 11, and the auxiliary hammer 21 moves forward by the movement amount N with respect to the carrier 16.
  • the movement amount M of the main hammer 20 reaches a distance corresponding to the maximum engagement length between the hammer claws 20a and the anvil claws 22b, the engagement between the hammer claws 20a and the anvil claws 22b. The match is released.
  • the movement amount M of the main hammer 20 reaches a distance corresponding to the maximum engagement length between the hammer claw 20a and the anvil claw 22b.
  • the first cam structure and the second cam structure are formed.
  • the movement amount M of the main hammer 20 in the rotation axis direction and the movement amount N of the sub hammer 21 in the rotation axis direction are respectively defined by the shapes of the first cam structure and the second cam structure. Since the ratio of the amount of movement for canceling the vibration in the axial direction preferably depends on the mass ratio of the main hammer 20 and the secondary hammer 21, the shapes of the first cam structure and the second cam structure are the main hammer. It is designed according to the mass ratio between 20 and the secondary hammer 21.
  • the mass of the main hammer 20 is P
  • the mass of the auxiliary hammer 21 is Q.
  • the mass P is smaller than the mass Q.
  • the first cam structure and the second cam groove 16a so that the movable range in the rotation axis direction of the steel ball 17 is smaller than the movable range in the rotation axis direction of the steel ball 19 in the first guide groove 11b.
  • a second cam structure is formed. This is because the mass Q of the secondary hammer 21 is larger than the mass P of the primary hammer 20, and vibrations caused by the movement of the primary hammer 20 in the rotational axis direction are opposite to the secondary hammer 21 having a large mass and have a small stroke. The purpose is to cancel the vibration caused by the movement.
  • the ratio of the movable range in the rotation axis direction of the steel ball 17 and the movable range in the rotation axis direction of the steel ball 19 is substantially equal to the ratio of the mass P of the main hammer 20 and the mass Q of the auxiliary hammer 21. May be set.
  • the length of the inclined groove of the second guide groove 16a in the rotational axis direction is made longer than the length of the inclined groove of the first guide groove 11b in the rotational axis direction. Can also be shortened. This realizes a shorter axis of the tool body and contributes to reducing the size and weight of the rotary impact tool 1.
  • the shape of the inclined groove in the movable range in the first cam structure and the second cam structure is determined by the design concept. That is, the ratio of the movement amount N of the secondary hammer 21 relative to the carrier 16 to the movement amount M of the primary hammer 20 relative to the spindle 11 is substantially equal to the ratio of the mass P of the primary hammer 20 and the mass Q of the secondary hammer 21.
  • the first cam structure and the second cam structure are formed. Thereby, it acts so that the vibration of the rotation axis direction by the main hammer 20 and the sub hammer 21 may mutually cancel, and it becomes possible to improve a user's workability
  • a rotary impact tool (1) includes a drive unit (10), a spindle (11) rotated by the drive unit, and a rotation axis of the spindle that is rotatable about the rotation axis.
  • a first hammer structure in which a first steel ball (19) is disposed between a main hammer (20), a first guide groove (11b) on the spindle side, and a first engagement groove (20b) on the main hammer side;
  • a second cam structure including a second steel ball (17) for supporting the auxiliary hammer.
  • the rotary impact tool of this aspect is configured such that when the main hammer moves in the rotation axis direction, the sub hammer moves in the direction opposite to the movement direction of the main hammer.
  • three or more second cam structures are provided, and the auxiliary hammer is supported by the second steel balls included in the three or more second cam structures.
  • the three or more second cam structures may be provided side by side in the circumferential direction. At this time, it is preferable that three or more second cam structures are provided side by side at equal intervals.
  • the secondary hammer may be supported in the rotation axis direction by three or more second steel balls.
  • the present invention can be used for a tool such as a rotary impact tool.

Abstract

L'invention concerne un outil (1) à percussion rotative, lequel comporte: un marteau principal (20) pouvant pivoter autour de l'axe de rotation d'une broche (11) et pouvant se déplacer en direction de cet axe de rotation; une première structure de came dans laquelle une bille d'acier (19) est située entre une première rainure (11b) de guidage côté broche et une première rainure (20b) de mise en prise côté marteau principal; une enclume (22) à laquelle la force de percussion rotative est appliquée par le marteau principal (20); un marteau secondaire (21) rotatif de façon solidaire avec le marteau principal (20); une deuxième structure de came dans laquelle une bille d'acier (17) supporte le marteau secondaire (21) de façon qu'il puisse pivoter autour de l'axe de rotation de la broche (11) et de façon qu'il puisse se déplacer en direction de cet axe de rotation. Cet outil (1) à percussion rotative est configuré de façon que lorsque le marteau principal (20) se déplace dans la direction de l'axe de rotation, le marteau secondaire (21) se déplace en direction opposée à la direction de déplacement du marteau principal (20). Cet outil comporte au moins trois deuxièmes structures de came et le marteau secondaire (21) est supporté par une bille d'acier contenue dans ces deuxièmes structures de came.
PCT/JP2017/024811 2016-09-27 2017-07-06 Outil à percussion rotative WO2018061388A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2016-188780 2016-09-27
JP2016188780A JP2018051660A (ja) 2016-09-27 2016-09-27 回転打撃工具

Publications (1)

Publication Number Publication Date
WO2018061388A1 true WO2018061388A1 (fr) 2018-04-05

Family

ID=61759392

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2017/024811 WO2018061388A1 (fr) 2016-09-27 2017-07-06 Outil à percussion rotative

Country Status (2)

Country Link
JP (1) JP2018051660A (fr)
WO (1) WO2018061388A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6979605B2 (ja) * 2018-05-11 2021-12-15 パナソニックＩｐマネジメント株式会社 インパクト回転工具

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010140268A1 (fr) * 2009-06-03 2010-12-09 株式会社空研 Clé à chocs
JP2014240108A (ja) * 2013-06-12 2014-12-25 パナソニック株式会社 インパクトレンチ
JP2016117140A (ja) * 2014-12-22 2016-06-30 株式会社Ｔｊｍデザイン 回転工具

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010140268A1 (fr) * 2009-06-03 2010-12-09 株式会社空研 Clé à chocs
JP2014240108A (ja) * 2013-06-12 2014-12-25 パナソニック株式会社 インパクトレンチ
JP2016117140A (ja) * 2014-12-22 2016-06-30 株式会社Ｔｊｍデザイン 回転工具

Also Published As

Publication number Publication date
JP2018051660A (ja) 2018-04-05

Similar Documents

Publication Publication Date Title
JP6832509B2 (ja) 回転打撃工具
US8490714B2 (en) Impact wrench
JP6027946B2 (ja) インパクトレンチ
US7048075B2 (en) Power tool
JP2017159418A (ja) インパクト回転工具
JP5583500B2 (ja) 打撃工具
JP6397325B2 (ja) 回転工具
EP2883657A2 (fr) Outil d'impact rotatif
JP6341283B2 (ja) 打撃工具
WO2018061389A1 (fr) Outil à percussion rotative
WO2018061388A1 (fr) Outil à percussion rotative
WO2018142742A1 (fr) Outil rotatif à percussion
WO2018061387A1 (fr) Outil à percussion rotative
JP2009172732A (ja) インパクト回転工具
JP6607502B2 (ja) インパクト回転工具
JP2013022691A (ja) インパクト回転工具
JP4283166B2 (ja) 回転打撃工具の騒音防止装置
JP2018051713A (ja) 電動工具
JP2010036282A (ja) 電動工具

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: 17855347

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 17855347

Country of ref document: EP

Kind code of ref document: A1