WO2015182512A1

WO2015182512A1 - Impact tool

Info

Publication number: WO2015182512A1
Application number: PCT/JP2015/064757
Authority: WO
Inventors: 西河　智雅; 哲祐原田; 松野　智
Original assignee: 日立工機株式会社
Priority date: 2014-05-30
Filing date: 2015-05-22
Publication date: 2015-12-03

Abstract

In order to make assembly of an impact driver more efficient while allowing sufficient mitigation of vibrations and reduction of weight to be achieved, three each of first engagement pawls (30e) and second engagement pawls (18d) for generating a striking force are disposed, and the relative play angle between a hammer (30) and anvil (18) along a rotating direction of a spindle is set to 90 degrees or smaller. This allows the weight of the impact driver to be reduced more than before while sufficiently mitigating vibrations generated by the impact driver. In addition, because the distance between adjoining first engagement pawls (30e) can be made longer than before, assembly of the impact driver including work such as installing steel balls can be made more efficient.

Description

Impact tool

The present invention includes an output member that is rotated by a rotating member, and a striking member that is provided between the rotating member and the output member, and that converts the rotational force of the rotating member into a striking force in the rotational direction of the output member. Related to tools.

2. Description of the Related Art Conventionally, an impact tool including an impact member that converts a rotational force of a rotary member rotated by a drive source into an impact force in the rotation direction of an output member is known. An example of this striking tool is described in Patent Document 1. The impact tool described in Patent Document 1 is provided between a spindle (rotating member) to which the rotational force of a driving source is transmitted, and between the spindle and the anvil (output member), and the rotational force of the spindle is used to rotate the anvil. And a hammer (a striking member) that converts it into a striking force.

A pair of spindle cams (grooves) are provided on the outer peripheral part of the spindle, and a pair of hammer cams (grooves) are provided on the inner peripheral part of the hammer, and steel balls (steel balls) are respectively provided between these cams. Has been placed. Further, four hammer claws arranged at equal intervals in the circumferential direction are provided on the anvil side of the hammer, and four anvil claws arranged at equal intervals in the circumferential direction are provided on the hammer side of the anvil. Yes. The hammer claws and the 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 rotational force of the drive source is transmitted to the tip tool via the spindle, steel ball, hammer and anvil. When a predetermined load is applied to the tip tool, the steel ball rolls following the spindle cam and the hammer cam. Thus, 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. At this time, 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.

Japanese Utility Model Publication No. 01-170570

However, in the hitting tool described in the above-mentioned Patent Document 1, there are four hammer claws and four anvil claws, which is advantageous for reducing the vibration of the hitting tool by improving the rotation balance. There has been a problem that it is difficult to make more lightweight. Moreover, since the distance between adjacent hammer claws is short, there is also a problem that it becomes difficult to incorporate the steel ball into the hammer cam from between the hammer claws.

The objective of this invention is providing the impact tool which can improve assembly workability | operativity, implement | achieving sufficient vibration reduction and weight reduction of a product.

In one aspect of the present invention, an output member rotated by a rotating member, and provided between the rotating member and the output member, the rotating force of the rotating member is converted into a striking force in the rotating direction of the output member. A striking tool including three first engaging claws provided side by side in the circumferential direction on the output member side of the striking member, and a striking member side of the output member in the circumferential direction. A second engaging claw that is provided side by side and that engages with each of the first engaging claws and transmits the rotational force of the striking member to the output member, and follows the rotational direction of the rotating member. A relative play angle between the striking member and the output member is 90 degrees or less.

In another aspect of the invention, the play angle is 30 degrees or more.

In another aspect of the present invention, an output member rotated by a rotating member, and provided between the rotating member and the output member, the rotational force of the rotating member is converted into a striking force in the rotational direction of the output member. A striking tool comprising: a first engaging claw provided in a row in the circumferential direction on the output member side of the striking member; and a circumferential direction on the striking member side of the output member. Are arranged side by side, and are respectively engaged with the first engaging claws to transmit the rotational force of the striking member to the output member. The relative play angle between the hitting member and the output member along is approximately 60 degrees.

In another aspect of the present invention, an output member rotated by a rotating member, and provided between the rotating member and the output member, the rotational force of the rotating member is converted into a striking force in the rotational direction of the output member. A striking tool comprising: a first engaging claw provided in a row in the circumferential direction on the output member side of the striking member; and a circumferential direction on the striking member side of the output member. And a second engagement claw that engages with each of the first engagement claws and transmits a rotational force of the striking member to the output member, and is provided on a radially outer side of the striking member. And the width dimension of the first engagement claw in the direction along the circumferential direction is 5.5 mm or more, and the width dimension of the second engagement claw in the direction along the circumferential direction outside the output member in the radial direction is 4. 0 mm or more.

In another aspect of the present invention, the width dimension of the first engagement claw is 15.5 mm or less, and the width dimension of the second engagement claw is 14.0 mm or less.

In another aspect of the present invention, an output member rotated by a rotating member, and provided between the rotating member and the output member, the rotational force of the rotating member is converted into a striking force in the rotational direction of the output member. A striking tool comprising: a first engaging claw provided in a row in the circumferential direction on the output member side of the striking member; and a circumferential direction on the striking member side of the output member. And a second engagement claw that engages with each of the first engagement claws and transmits a rotational force of the striking member to the output member, and is provided on a radially outer side of the striking member. The width dimension of the first engagement claw in the direction along the circumferential direction is approximately 10.0 mm, and the width dimension of the second engagement claw in the direction along the circumferential direction outside the output member in the radial direction is approximately 8 mm. .5 mm.

According to the present invention, three first engaging claws and three second engaging claws for generating a striking force are provided, and the relative play angle between the striking member and the output member along the rotation direction of the rotating member is 90. Be less than 1 degree.

Thereby, weight reduction of a hitting tool can be attained compared with before, fully reducing the vibration which a hitting tool generates.

Moreover, since the distance between the adjacent first engaging claws can be made longer than before, it is possible to improve the assembling workability of the impact tool such as the incorporation of a steel ball.

It is a perspective view which shows the impact tool of this invention. It is a fragmentary sectional view of the impact tool of FIG. FIG. 3 is an exploded perspective view of the striking mechanism according to the first embodiment. 3A is a view of the striking mechanism of FIG. 3 viewed from a direction orthogonal to the axial direction, FIG. 3B is a view of the striking mechanism of FIG. 3 viewed from the axial direction, and FIG. It is the figure which expand | deployed the 2nd engaging claw in the circumferential direction. It is explanatory drawing explaining the assembly procedure of the steel ball with respect to a hammer cam. It is explanatory drawing explaining the processing procedure of a hammer. (A), (b), (c) is the figure corresponding to FIG. 4 which shows the striking mechanism of Embodiment 2. FIG. (A), (b), (c) is the figure corresponding to FIG. 4 which shows the striking mechanism of Embodiment 3. FIG. (A), (b), (c) is the figure corresponding to FIG. 4 which shows the striking mechanism of Embodiment 4. FIG. (A), (b), (c) is the figure corresponding to FIG. 4 which shows the striking mechanism of Embodiment 5. FIG.

Hereinafter, Embodiment 1 of the present invention will be described in detail with reference to the drawings.

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, and FIG. 3 is a view of the striking mechanism of FIG. 3 viewed from a direction orthogonal to the axial direction, FIG. 3B is a view of the striking mechanism of FIG. 3 viewed from the axial direction, and FIG. FIG. 5 is an explanatory diagram for explaining the procedure for assembling the steel ball to the hammer cam, and FIG. 6 is an explanatory diagram for explaining the hammer processing procedure.

As shown in FIGS. 1 and 2, an impact driver 10 as a striking tool includes a battery pack 11 that houses a battery cell that can be charged and discharged, and an electric motor that is driven by power supplied from the battery pack 11. 12. 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.

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 rotating shaft 14 can be switched by operating a changeover switch 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. The anvil 18 is rotatably supported by a sleeve 19 mounted inside the casing 13. 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 inside the casing 13 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 a carrier 25 that supports each planetary gear 24 so that it can rotate and revolve. The ring gear 23 is fixed to the casing 13 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. Is formed.

Inside the casing 13 and between the electric motor 12 and the speed reducer 21 in the direction along the axis A, a holder member 27 formed in a substantially bowl shape is provided. A bearing 28 is attached to the center portion of the holder member 27, and this bearing 28 rotatably supports a proximal end portion of the spindle 26 on the electric motor 12 side. A pair of (two) groove-like spindle cams 26b are provided around the spindle 26 on the anvil 18 side. A part of a steel ball (steel ball) 29 enters each of the spindle cams 26b.

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 18 b is opened toward the outside of the casing 13 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 hammer 30 is rotatable relative to the spindle 26 and is relatively movable in the direction along the axis A. A pair of (two) groove-shaped hammer cams 30 a extending in the direction along the axis A are formed on the inner side in the radial direction of the hammer 30. A part of each steel ball 29 enters each of the hammer cams 30a.

In this way, one of the two spindle cams 26b and one hammer cam 30a are used as one set, and one of the two steel balls 29 is held. In addition, the other one of the two spindle cams 26b and the other hammer cam 30a is set as one set, and the other two steel balls 29 are held. Here, 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.

Here, 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. When the load in the rotational direction of the anvil 18 increases, the first engagement claw 30e of the hammer 30 and the second engagement claw 18d of the anvil 18 (both see FIGS. 3 and 4) are released and engaged. Are repeated at a high speed, thereby generating a striking force on the tip tool 17. Here, the weight of the hammer 30 is set to be larger than the weight of the anvil 18, and the hammer 30 converts the rotational force of the spindle 26 into a striking force in the rotational direction of the anvil 18.

Next, the engagement structure between the hammer 30 and the anvil 18 will be described in detail with reference to FIGS. 3 and 4.

The hammer 30 includes a main body 30b formed in a substantially cylindrical shape. A mounting hole that extends in a direction along the axis A and is rotatably mounted on the spindle 26 is radially inward of the main body 30b. 30c is provided. 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. Here, the diameter dimension of the main body 30b on the spindle 26 side (large diameter side) is set to about 40 mm.

An opposing plane 30d that faces the anvil 18 is provided on the anvil 18 side of the main body 30b, and three first engaging claws 30e that protrude toward the anvil 18 in the direction along the axis A are provided on the opposing plane 30d. It is provided integrally. These first engaging claws 30e are arranged side by side at equal intervals (120 degree intervals) along the circumferential direction of the opposing flat surface 30d, and the cross-sectional shape along the direction intersecting the axis A is substantially fan-shaped. The distal end side of the first engaging claw 30e 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 mounting hole 30c.

A first contact plane SF1 is provided on one side of the first engagement claw 30e along the circumferential direction of the hammer 30. A second contact plane SF2 is provided on the other side of the first engagement claw 30e along the circumferential direction of the hammer 30. And each 4th contact plane SF4 of the 2nd engaging claw 18d of the anvil 18 mentioned later contacts each 1st contact plane SF1, and the 2nd engagement of the anvil 18 touches each 2nd contact plane SF2. Each third contact plane SF3 of the joint claw 18d comes into contact with the entire surface.

Moreover, the width dimension of the 1st engaging claw 30e of the direction outside the diameter direction of the hammer 30 and the circumferential direction is set to 10.0 mm as shown in FIG.4 (c). As a result, the second engaging claws 18d of the anvil 18 can enter between the first engaging claws 30e adjacent in the circumferential direction of the hammer 30 with a margin.

As shown in FIG. 5, the line segment connecting the first contact plane SF <b> 1 and the second contact plane SF <b> 2 of the first engaging claws 30 e adjacent along the circumferential direction of the hammer 30 is the axis line A of the hammer 30. A straight line L extending straight in the intersecting direction is formed. That is, since the three first engaging claws 30e are provided on the hammer 30, three straight lines L are formed.

Thus, the first and second contact planes SF1 and SF2 of the three first engaging claws 30e are arranged on the three straight lines L, respectively. Therefore, in the present embodiment, as shown in FIG. 6, the hammer 30 can be easily processed. Specifically, as shown in FIG. 6, a cutting tool T provided with a twist drill D is used, and the cutting tool T is moved along a broken line arrow M <b> 1 from a direction intersecting the axis A of the hammer 30. D is moved along the straight line L. Then, by repeating this operation for the number of straight lines L (three times), the first and second contact planes SF1 and SF2 (total of six surfaces) of the three first engagement claws 30e are formed. Thus, since it is not necessary to form each of the first engaging claws 30e individually, the processing time of the hammer 30 can be greatly shortened and its workability can be improved.

As shown in FIG. 5, end portions of a pair of hammer cams 30 a formed on the radially inner side of the hammer 30 are opened on the opposing plane 30 d of the hammer 30. The shape of the opening side of these hammer cams 30a is formed in a substantially arc shape in cross section. The pair of hammer cams 30a are opposed to each other with the mounting hole 30c as a center, and a recess 30f for incorporating the steel ball 29 is provided at the top of each hammer cam 30a. Between each hammer cam 30a, a pair of projections 30g projecting inward in the radial direction of the hammer 30 is provided, and the tip side of these projections 30g faces the mounting hole 30c, and the boundary of each hammer cam 30a. Forming part.

As described above, since the three first engaging claws 30e are provided on the opposing plane 30d of the hammer 30 and the ends of the pair of (two) hammer cams 30a are opened, it is adjacent along the circumferential direction of the hammer 30. A pair of recessed portions 30f can be disposed between the matching first engaging claws 30e. In this case, since the distance between the adjacent first engaging claws 30e can be made longer than before, the work of assembling each steel ball 29 into each hammer cam 30a can be easily performed.

The anvil 18 includes a main body portion 18c formed in a substantially cylindrical shape. On the hammer 30 side along the axial direction of the main body portion 18c, three second engaging claws 18d protruding outward in the radial direction are provided. It is provided integrally. These second engagement claws 18d are arranged at equal intervals (120 degree intervals) 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 along the circumferential direction of the anvil 18 of the second engagement claw 18d. A fourth contact plane SF4 is provided on the other side of the second engagement claw 18d along the circumferential direction of the anvil 18. The second contact planes SF2 of the first engagement claws 30e of the hammer 30 are in contact with the entire third contact planes SF3, and the first engagement claws of the hammer 30 are in contact with the fourth contact planes SF4. Each first contact plane SF1 of 30e comes into contact with the entire surface.

Moreover, the width dimension of the 2nd engaging claw 18d of the direction along the radial direction outer side of the anvil 18 is set to 8.5 mm as shown in FIG.4 (c). That is, the width dimension is set slightly shorter than that of the first engagement claw 30e. Accordingly, the distance between the second engaging claws 18d adjacent to each other along the circumferential direction of the anvil 18 becomes a relatively long distance S1, and the first engaging claws 30e of the hammer 30 can enter with a margin. Yes.

Next, the state in which the first engagement claw 30e of the hammer 30 and the second engagement claw 18d of the anvil 18 are engaged will be described in detail with reference to FIG. 4 shows a state where the first contact plane SF1 of the first engagement claw 30e and the fourth contact plane SF4 of the second engagement claw 18d are in contact with each other over the entire surface. Here, the first engaging claws 30e and the second engaging claws 18d provided in three are respectively engaged and released simultaneously.

As shown in FIG. 4B, the second engagement claw 18 d of the anvil 18 is movable between the first engagement claws 30 e adjacent along the circumferential direction of the hammer 30. Specifically, the hammer 30 is rotated forward so that the first contact plane SF1 of the first engagement claw 30e and the fourth contact plane SF4 of the second engagement claw 18d are in contact with each other (shown by a solid line in the figure). From the first state, the hammer 30 is reversed so that the second contact plane SF2 of the first engagement claw 30e and the third contact plane SF3 of the second engagement claw 18d are in contact with each other (shown by a broken line in the figure) In the second state, the second engagement claw 18d is movable. Here, between the adjacent first engaging claws 30e, the angle formed when the second engaging claws 18d are in the first state and the second state is the striking member (hammer 30) and the output member in the present invention. A relative play angle with (anvil 18) is formed.

In the striking mechanism SM including the hammer 30 and the anvil 18 according to Embodiment 1, the relative play angle between the hammer 30 and the anvil 18 is set to 60 degrees or less and 60 degrees or more and 30 degrees or more. This is because both the hammer 30 and the anvil 18 are provided with three first engagement claws 30e and three second engagement claws 18d at intervals of 120 degrees along the circumferential direction, and the first engagement. This is because the width dimension of the claw 30e is set to 10.0 mm and the width dimension of the second engagement claw 18d is set to 8.5 mm.

Here, in order to assemble the striking mechanism SM, first, the spindle 26, the hammer 30, and the anvil 18 are arranged coaxially along the axis A as shown in FIG. Thereafter, the spindle 26 is mounted in the mounting hole 30c of the hammer 30 under this state. When the spindle 26 is mounted on the hammer 30, an annular plate 31 and a coil spring 32 (see FIG. 2) are incorporated between the two.

Next, as shown by a broken line arrow M <b> 2 in FIG. 5, the pair of steel balls 29 are mounted between the hammer 30 and the spindle 26 so as to face the pair of depressions 30 f. Thereby, the steel balls 29 are respectively incorporated between the hammer cams 30a and the spindle cams 26b. Thereafter, the shaft portion 26a of the spindle 26 protruding toward the opposing flat surface 30d of the hammer 30 is mounted in the holding hole 18a (see FIG. 2) of the anvil 18. Thereby, the striking mechanism SM is completed.

Next, the operation of the impact driver 10 will be described in detail with reference to the drawings.

When the electric motor 12 is stopped, the hammer 30 pressed by the coil spring 32 contacts the anvil 18 and stops. When electric power is supplied to the electric motor 12 and the rotating shaft 14 rotates, the torque (rotational force) of the rotating shaft 14 is transmitted to the sun gear 22 of the speed reducer 21. When torque is transmitted to the sun gear 22, the ring gear 23 becomes a reaction force element, and the carrier 25 becomes an output element. That is, the torque of the sun gear 22 is transmitted to the carrier 25, the rotational speed of the carrier 25 becomes lower than the rotational speed of the sun gear 22, and the torque is amplified.

When torque is transmitted to the carrier 25, the spindle 26 rotates together with the carrier 25. The torque of the spindle 26 is transmitted to the hammer 30 via the steel ball 29. The torque of the hammer 30 is transmitted to the anvil 18 by the engagement of the three first engaging claws 30e and the three second engaging claws 18d, whereby the anvil 18 is rotated. The torque transmitted to the anvil 18 is transmitted to a bolt (not shown) via the tip tool 17, and the bolt is screwed into an object such as wood.

In a state where the torque required to rotate the tip tool 17 is low, that is, in a low load state, as shown in FIG. 4, the first contact plane SF1 of the first engagement claw 30e and the second engagement claw 18d. The fourth contact plane SF4 is in contact with the fourth contact plane SF4. Thereafter, when the bolt is screwed into the wood and the frictional resistance between the wood and the bolt increases, for example, the torque required to rotate the tip tool 17 increases, the anvil 18 stops. Thereby, each steel ball 29 rolls inside each hammer cam 30 a and each spindle cam 26 b, and as a result, the hammer 30 moves along the axis A so as to be separated from the anvil 18.

As a result, as shown by a broken line arrow M3 in FIG. 4C, the first engagement claw 30e and the second engagement claw 18d are disengaged and released from each other, and the torque of the hammer 30 is transmitted to the anvil 18. It will not be done. Thereafter, the end of the hammer 30 on the electric motor 12 side collides with the stopper 33, and the stopper 33 absorbs the kinetic energy of the hammer 30.

Thereafter, the rotation of the hammer 30 is continued, and when the first engagement claw 30e gets over the second engagement claw 18d as shown by the broken line arrow M3 in FIG. 4C, the hammer 30 of the coil spring 32 is moved. The pressing force increases. Thereby, each steel ball 29 rolls inside each hammer cam 30a and each spindle cam 26b, and the hammer 30 is moved so as to be close to each other while rotating relative to the anvil 18.

Thereafter, the respective first engaging claws 30e of the rotating hammer 30 collide simultaneously with the respective second engaging claws 18d of the stopped anvil 18, and the striking force is exerted in the rotational direction of the anvil 18 and the tip tool 17. Is added. Here, when the rotation direction of the electric motor 12 is reversed by operating the changeover switch 16 (see FIG. 2), a striking force can be applied in a direction opposite to the above-described operation. Thereby, the tightened bolt can be loosened.

As described above in detail, according to the impact driver 10 according to the present embodiment, three first engagement claws 30e and three second engagement claws 18d that generate a striking force are provided, and the rotation direction of the spindle 26 is determined. The relative play angle between the hammer 30 and the anvil 18 is set to 90 degrees or less.

Thereby, weight reduction of the impact driver 10 can be achieved compared with the past, fully reducing the vibration which the impact driver 10 generate | occur | produces.

Further, since the distance between the adjacent first engaging claws 30e can be made longer than before, the assembly workability of the impact driver 10 such as the incorporation of the steel ball 29 can be improved.

Further, in the present embodiment, (1) the diameter of the main body 30b is "about 40 mm", (2) the relative play angle between the hammer 30 and the anvil 18 is "60 degrees", and (3) the first The width dimension of the engaging claw 30e is set to “10.0 mm”, and (4) the width dimension of the second engaging claw 18d is set to “8.5 mm”.

Therefore, the first and second contact planes SF1 and SF2 of the three first engagement claws 30e are shown in FIG. 5 while the strength of the first engagement claws 30e and the second engagement claws 18d is sufficient. In addition, each can be arranged on three straight lines L. Therefore, the hammer 30 can be easily processed as shown in FIG.

Next, 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.

7A, 7B, and 7C show views corresponding to FIG. 4 showing the striking mechanism of the second embodiment.

As shown in FIG. 7, the striking mechanism SM of the second embodiment has a shape of the first engaging claw 30e of the hammer (striking member) 130 as compared with the striking mechanism SM (see FIG. 4) of the first embodiment. And only the shape of the second engagement claw 18d of the anvil (output member) 118 is different.

Specifically, in the second embodiment, (1) the diameter of the main body 30b is “about 40 mm”, (2) the relative play angle between the hammer 130 and the anvil 118 is “90 degrees”, (3 ) The width dimension of the first engagement claw 30e is set to “5.5 mm”, and (4) the width dimension of the second engagement claw 18d is set to “4.0 mm”.

Here, the relative play angle between the hammer 130 and the anvil 118 is set to “90 degrees”. This is because the width dimension of the first engagement claw 30e is set to 5.5 mm, and the second engagement claw 18d. This is due to the fact that the width dimension of is set to 4.0 mm.

The width dimension of the first engagement claw 30e and the width dimension of the second engagement claw 18d are significantly narrower than those of the first embodiment. This is the narrowest dimension in which the first engagement claw 30e and the second engagement claw 18d can be stably manufactured without variation. In other words, the hammer 130 and the anvil 118 are formed by casting, forging, cutting, etc., respectively. If the width is further narrowed, the first engaging claw 30e and the second engaging claw 18d are formed. This is a dimension that can cause defects such as “chips” of the nails in the machining process.

Here, in order to increase the strength of the first engagement claw 30e and the second engagement claw 18d, the first engagement claw 30e of the hammer 130 and the second engagement claw 18d of the anvil 118 in the second embodiment are carburized. It is desirable to perform surface hardening treatment such as pouring and electrolytic nickel plating.

In the second embodiment formed as described above, the same operational effects as those of the first embodiment described above can be obtained. In addition, in the second embodiment, the first engaging claw 30e and the second engaging claw 18d are set to be narrower, so that the product can be made lighter than the first embodiment. It becomes possible. Further, the distance S2 between the second engaging claws 18d adjacent to each other along the circumferential direction of the anvil 118 can be made longer than the distance S1 (see FIG. 4) of the first embodiment (S2> S1). Thereby, the 1st engagement nail | claw 30e of the hammer 130 can be moved along the broken-line arrow M4, and a striking force can be reliably given to the rotation direction of the anvil 118.

Next, Embodiment 3 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.

FIGS. 8A, 8B, and 8C are views corresponding to FIG. 4 showing the striking mechanism of the third embodiment.

As shown in FIG. 8, the striking mechanism SM of the third embodiment has a shape of the first engaging claw 30e of the hammer (striking member) 230 as compared with the striking mechanism SM (see FIG. 4) of the first embodiment. And only the shape of the second engaging claw 18d of the anvil (output member) 218 is different.

Specifically, in the third embodiment, (1) the diameter of the main body 30b is “about 40 mm”, (2) the relative play angle between the hammer 230 and the anvil 218 is “30 degrees”, (3 ) The width dimension of the first engagement claw 30e is set to “15.5 mm”, and (4) the width dimension of the second engagement claw 18d is set to “14.0 mm”.

Here, the relative play angle between the hammer 230 and the anvil 218 is set to “30 degrees”. This is because the width dimension of the first engagement claw 30e is set to 15.5 mm, and the second engagement claw 18d. This is because the width dimension of is set to 14.0 mm.

The width dimension of the first engagement claw 30e and the width dimension of the second engagement claw 18d are much wider than those of the first embodiment. This is the widest dimension that can transmit the striking force of the hammer 230 to the anvil 218 when the striking mechanism SM is in operation. That is, if the width is further increased, the first engagement claw 30e cannot enter between the adjacent second engagement claws 18d with a margin. For example, the corner C1 of the first engagement claw 30e and the second This is a dimension that may cause a defect such as “chip” due to the collision with the corner C2 of the engaging claw 18d.

Also in the third embodiment formed as described above, the same operational effects as those of the first embodiment described above can be obtained. In addition, in the third embodiment, the first engagement claw 30e and the second engagement claw 18d are set wider, respectively, so that the first engagement claw 30e and The inertia (moment of inertia) of the second engaging claws 18d can be increased. Therefore, the striking force in the rotation direction of the anvil 218 can be made stronger.

The distance S3 between the second engaging claws 18d adjacent to each other along the circumferential direction of the anvil 218 is shorter than the distance S1 (see FIG. 4) of the first embodiment (S3 <S1). It is sufficiently longer than the width dimension of the joint claw 30e. Therefore, the first engaging claw 30e of the hammer 230 is moved along the broken line arrow M5 so that a striking force is reliably applied in the rotation direction of the anvil 218.

Next, a fourth embodiment 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.

FIGS. 9A, 9B and 9C show views corresponding to FIG. 4 showing the striking mechanism of the fourth embodiment.

As shown in FIG. 9, the striking mechanism SM of the fourth embodiment has a shape of the first engaging claw 30 e of the hammer (striking member) 330 as compared with the striking mechanism SM (see FIG. 4) of the first embodiment. And only the shape of the second engaging claw 18d of the anvil (output member) 318 is different.

Specifically, in the fourth embodiment, (1) the diameter of the main body 30b is “about 40 mm”, (2) the relative play angle between the hammer 330 and the anvil 318 is “75 degrees”, (3 ) The width dimension of the first engagement claw 30e is set to “7.0 mm”, and (4) the width dimension of the second engagement claw 18d is set to “6.5 mm”.

Here, the relative play angle between the hammer 330 and the anvil 318 is set to “75 degrees”. This is because the width dimension of the first engagement claw 30e is set to 7.0 mm, and the second engagement claw 18d. This is because the width dimension is set to 6.5 mm.

The width dimension of the first engagement claw 30e and the width dimension of the second engagement claw 18d are slightly narrower than those in the first embodiment. In the fourth embodiment, the numerical values such as the dimensions realize a light weight while ensuring sufficient practical strength for the striking mechanism SM, and cause defects in the processing process (such as “chips” of the nails). The value is advantageous in that it can be reliably prevented. However, also in the present embodiment, it is desirable to subject the first engaging claws 30e of the hammer 330 and the second engaging claws 18d of the anvil 318 to surface hardening treatment such as carburizing and quenching or electrolytic nickel plating.

In the fourth embodiment formed as described above, the same operational effects as those of the first embodiment can be obtained. In addition, in the fourth embodiment, the first engaging claw 30e and the second engaging claw 18d are set slightly narrower, so that the product can be made lighter than in the first embodiment. it can. Further, the distance S4 between the second engaging claws 18d adjacent to each other along the circumferential direction of the anvil 318 can be made slightly longer than the distance S1 (see FIG. 4) of the first embodiment (S4> S1). . Thereby, the 1st engagement nail | claw 30e of the hammer 330 can be moved along the broken-line arrow M6, and a striking force can be reliably given to the rotation direction of the anvil 318.

Next, a fifth embodiment 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.

FIGS. 10A, 10B and 10C show views corresponding to FIG. 4 showing the striking mechanism of the fifth embodiment.

As shown in FIG. 10, the striking mechanism SM of the fifth embodiment has a shape of the first engaging claw 30e of the hammer (striking member) 430 as compared with the striking mechanism SM (see FIG. 4) of the first embodiment. And only the shape of the second engagement claw 18d of the anvil (output member) 418 is different.

Specifically, in the fifth embodiment, (1) the diameter of the main body 30b is “about 40 mm”, (2) the relative play angle between the hammer 430 and the anvil 418 is “65 degrees”, (3 ) The width dimension of the first engagement claw 30e is set to “9.0 mm”, and (4) the width dimension of the second engagement claw 18d is set to “7.5 mm”.

Here, the relative play angle between the hammer 430 and the anvil 418 is set to “65 degrees”. This is because the width dimension of the first engagement claw 30e is set to 9.0 mm, and the second engagement claw 18d. This is because the width dimension is set to 7.5 mm.

The width dimension of the first engagement claw 30e and the width dimension of the second engagement claw 18d are slightly narrower than those in the first embodiment. The numerical values such as the dimensions in the fifth embodiment are obtained by hitting the first engaging claws 30e of the hammer 430 and the second engaging claws 18d of the anvil 418 without subjecting them to surface hardening treatment such as carburizing and quenching or electrolytic nickel plating. The mechanism SM is a numerical value that provides sufficient practical strength.

In the fifth embodiment formed as described above, the same operational effects as those of the first embodiment described above can be obtained. In addition, in the fifth embodiment, since the first engagement claw 30e and the second engagement claw 18d are set slightly narrower, the weight of the product can be reduced as compared with the first embodiment. it can. Further, the distance S5 between the second engaging claws 18d adjacent to each other along the circumferential direction of the anvil 418 can be made slightly longer than the distance S1 (see FIG. 4) of the first embodiment (S5> S1). . Thereby, the 1st engagement nail | claw 30e of the hammer 430 can be moved along the broken-line arrow M7, and a striking force can be reliably given to the rotation direction of the anvil 418.

It goes without saying that the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the scope of the invention. For example, the impact tool of the present invention includes an impact wrench and the like in addition to the impact driver 10 described above. Further, 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. Furthermore, 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.

Furthermore, 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. Further, the impact tool of the present invention includes not only a structure in which the tip tool 17 is directly attached to the

anvils

18, 118, 218, 318, 418 but also a structure in which the tip tool is attached to the anvil via a socket, an adapter, or the like. .

DESCRIPTION OF SYMBOLS 10 ... Impact driver (blow tool), 11 ... Battery pack, 12 ... Electric motor, 13 ... Casing, 14 ... Rotating shaft, 15 ... Trigger switch, 16 ... Changeover switch, 17 ... Tip tool, 18 ... Anvil (output member) , 18a ... holding hole, 18b ... mounting hole, 18c ... main body part, 18d ... second engaging claw, 19 ... sleeve, 20 ... detaching mechanism, 21 ... reduction gear, 22 ... sun gear, 23 ... ring gear, 24 ... planetary gear, 25 ... carrier, 26 ... spindle (rotating member), 26a ... shaft, 26b ... spindle cam, 27 ... holder member, 28 ... bearing, 29 ... steel ball, 30 ... hammer (striking member), 30a ... hammer cam, 30b ... Body part, 30c ... mounting hole, 30d ... opposing plane, 30e ... first engaging claw, 30f ... hollow part, 30g ... projection, 31 ... annular plate, 3 ... coil spring, 33 ... stopper, 118 ... anvil (output member), 130 ... hammer (blow member), 218 ... anvil (output member), 230 ... hammer (batter member), 318 ... anvil (output member), 330 ... Hammer (striking member), 418 ... anvil (output member), 430 ... hammer (striking member), C1, C2 ... corner, D ... twist drill, SF1 ... first contact plane, SF2 ... second contact plane, SF3 ... Third contact plane, SF4 ... fourth contact plane, SM ... striking mechanism, T ... cutting tool

Claims

A striking member having an output member rotated by a rotating member, and a striking member that is provided between the rotating member and the output member and converts a rotational force of the rotating member into a striking force in a rotation direction of the output member. A first engaging claw provided in a row in the circumferential direction on the output member side of the striking member, and three in the circumferential direction on the striking member side of the output member, A second engaging claw that engages with each of the first engaging claws and transmits a rotational force of the striking member to the output member, and the striking member and the output member along a rotation direction of the rotating member. The impact tool whose relative play angle is 90 degrees or less.
The impact tool according to claim 1, wherein the play angle is 30 degrees or more.
A striking member having an output member rotated by a rotating member, and a striking member that is provided between the rotating member and the output member and converts a rotational force of the rotating member into a striking force in a rotation direction of the output member. A first engaging claw provided in a row in the circumferential direction on the output member side of the striking member, and three in the circumferential direction on the striking member side of the output member, A second engaging claw that engages with each of the first engaging claws and transmits a rotational force of the striking member to the output member, and the striking member and the output member along a rotation direction of the rotating member. The impact tool whose relative play angle is approximately 60 degrees.
A striking member having an output member rotated by a rotating member, and a striking member that is provided between the rotating member and the output member and converts a rotational force of the rotating member into a striking force in a rotation direction of the output member. A first engaging claw provided in a row in the circumferential direction on the output member side of the striking member, and three in the circumferential direction on the striking member side of the output member, A second engaging claw that engages with each of the first engaging claws to transmit the rotational force of the striking member to the output member, and is arranged in the direction along the circumferential direction on the radially outer side of the striking member. A striking tool in which the width dimension of the first engagement claw is 5.5 mm or more, and the width dimension of the second engagement claw in the direction along the circumferential direction on the radially outer side of the output member is 4.0 mm or more.
The impact tool according to claim 4, wherein a width dimension of the first engagement claw is 15.5 mm or less and a width dimension of the second engagement claw is 14.0 mm or less.
A striking member having an output member rotated by a rotating member, and a striking member that is provided between the rotating member and the output member and converts a rotational force of the rotating member into a striking force in a rotation direction of the output member. A first engaging claw provided in a row in the circumferential direction on the output member side of the striking member, and three in the circumferential direction on the striking member side of the output member, A second engaging claw that engages with each of the first engaging claws to transmit the rotational force of the striking member to the output member, and is arranged in the direction along the circumferential direction on the radially outer side of the striking member. A striking tool in which the width dimension of the first engagement claw is approximately 10.0 mm, and the width dimension of the second engagement claw in the direction along the circumferential direction on the radially outer side of the output member is approximately 8.5 mm.