JPH09272005A - Operation switching mechanism for rotary tool - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enhance the durability of a switching member, to eliminate the production of frictional sound during driving, to avoid deformation or a temperature-rise of a resin lever of the switching member, thereby insuring safety, in a rotary tool, for which three operation modes, or a drill mode, a hammer drill mode, and a hammer mode, can be switched with each other. SOLUTION: An intermediate shaft 2 rotates when a motor is driven, and the intermediate shaft 2 is provided with a first clutch 1 and a second clutch 5 in a freely rotatable manner. The first clutch 4 and the second clutch 5 are engaged with an intermediate shaft spline part 2T of the intermediate shaft 2. The rotation of the intermediate shaft 2 is transferred as rotating motion to a tool part via the second clutch 5 and a final gear 6, and it is transferred as impacting motion to the tool part via the first clutch 4 and a boss 3. In this case, a pin 7 does not touch any of the first clutch 4 and the second clutch 5. Owing to the pin 7, the engagement between the second clutch 5 and the intermediate shaft 2 is disengaged, and the engagement between the first clutch 4 and the intermediate shaft 2 is also disengaged.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary tool operation switching mechanism, and more particularly to a rotary tool switching mechanism capable of switching among three modes of a drill mode, a hammer drill mode and a hammer mode.

[0002]

[Prior art]

[First Conventional Example] As a rotary tool, there is a rotary tool capable of switching among three modes of a drill mode, a hammer mode, and a hammer drill mode. The drill mode is a mode in which the tool portion at the tip is rotated, and the hammer mode is a mode in which the tool portion is reciprocated in the axial direction to perform a striking operation. The hammer drill mode is a mode in which, while rotating the tool part, at the same time, the tool part is reciprocally moved in the axial direction to perform an impact operation.

As a rotary tool having this three-mode switching function, there is a technique disclosed in Japanese Patent Application Laid-Open No. 6-210507. This rotary tool switching function is shown in FIGS. 11 and 12. As shown in FIG. 11, the rotational drive of the motor is transmitted to the gear 9 via the pinion 16. The gear 9 is integrally fixed to the intermediate shaft 60, and the gear 9
The intermediate shaft 60 rotates along with the rotation.

A clutch 61 is splined to the intermediate shaft 60. That is, the clutch 61 is the intermediate shaft 60.
Is rotated with the rotation of and is held slidably in the directions of arrows 90 and 91. Fitting recesses 63 and 64 (FIG. 11B) are formed at both ends of the clutch 61. A transmission gear 66 is rotatably attached to the intermediate shaft 60. The final gear 6 is meshed with the transmission gear 66, and the rotation of the final gear 6 causes the tool portion to rotate.

The transmission gear 66 has a fitting projection 67 on the transmission gear side.
The transmission gear side fitting convex portion 67 is engageable with the fitting concave portion 63 formed in the clutch 61. FIG. 11A shows the drill mode, in which the clutch 61 moves in the direction of arrow 91, and the fitting recess 63 and the transmission gear side fitting projection 67 of the transmission gear 66 are engaged.

In the state shown in FIG. 11A, the transmission gear 66 also rotates in response to the rotation of the intermediate shaft 60 and the clutch 61. The final gear 6 is rotated by the rotation of the transmission gear 66, and the tool portion is rotated to operate in the drill mode.

A boss 3 is rotatably attached to the intermediate shaft 60. This boss 3 has a boss-side fitting projection 6
5 is formed, and can be engaged with the fitting recess 64 of the clutch 61. When the boss 3 is rotated, this rotational movement is transmitted to the arm 17 as reciprocating movement in the directions of arrows 90 and 91, and the reciprocating movement of the arm 17 causes the tool portion to perform a striking movement.

FIG. 11C shows the hammer mode in which the clutch 61 moves in the direction of arrow 90 and the fitting recess 64 and the boss-side fitting projection 65 of the boss 3 are engaged. In the state shown in FIG. 11C, the boss 3 also rotates in response to the rotation of the intermediate shaft 60 and the clutch 61. The arm 17 reciprocates due to the rotation of the boss 3, and the tool portion performs a striking operation to operate in a hammer mode.

FIG. 11B shows the hammer drill mode. The clutch 61 is at the intermediate position between FIGS. 11A and 11C, and both the transmission gear 66 and the boss 3 rotate as the clutch 61 rotates. As a result, the hammering motion is transmitted to the tool unit together with the rotating motion, and the tool unit strikes while rotating, and operates in the hammer drill mode.

As described above, the clutch 61 is connected to the intermediate shaft 60.
By controlling the movement in the directions of arrows 90 and 91 above,
Switch the mode. FIG. 12 shows a mechanism for moving the clutch 61 in the axial direction. A groove 62 is formed in the center of the clutch 61 in the circumferential direction. Then, the head portion 68 a of the eccentric pin 68 is fitted in the groove 62. The eccentric pin 68 is housed in the sleeve 73, and the eccentric pin 68 and the sleeve 73 are held in the bottomed hole 72 of the change lever body 71.

The change lever body 71 is rotated by operating a knob portion of the change lever located outside the housing. Since the eccentric pin 68 is provided at an eccentric position with respect to the rotation center of the change lever main body 71, the eccentric pin 6 is rotated as the change lever main body 71 rotates.
8 moves in the directions of arrows 90 and 91. That is, the clutch 61 can be controlled to move in the directions of arrows 90 and 91 by operating the knob portion of the change lever.
As shown in FIG. 11, a drill mode, a hammer drill and a hammer mode can be selected.

As shown in FIG. 12, in the bottomed hole 72 of the change lever body 71, between the sleeve 73 and
O-rings 69 and 70 are interposed. This O-ring 6
9 and 70, the fitting concave portion 63 or the fitting concave portion 64 of the clutch 61 has a transmission gear side fitting convex portion 67 and a boss side fitting convex portion 65.
It is designed to absorb the shock when it is fitted to and to switch modes smoothly.

[Second Conventional Example] FIGS. 13 and 14 show a second conventional example. The second conventional example is a rotary tool that switches between two modes, a drill mode and a hammer drill mode. As shown in FIG. 13A, the rotational drive from the motor is transmitted to the gear 9. The gear 9 is integrally fixed to the intermediate shaft 60, and the intermediate shaft 60 also rotates along with the gear 9. A pinion 83 is integrally formed on the intermediate shaft 60, and a gear for rotational drive is always meshed with the pinion 83 to transmit the rotational movement to the tool portion.

A clutch 87 is rotatably attached to the intermediate shaft 60, and the clutch 87 is movable on the intermediate shaft 60 in the directions of arrows 90 and 91. Further, the boss 3 is rotatably attached to the intermediate shaft 60, and the boss 3 transmits the rotational movement to the arm 17 as a reciprocating movement in the directions of arrows 90 and 91, and strikes the tool portion.

FIG. 13B shows details of the intermediate shaft 60. Splines 81 and 82 are formed on the intermediate shaft 60. On the other hand, as shown in FIG. 14E, splines 74 and 75 are formed on the inner circumference of the clutch 87. In addition,
14C is a cross-sectional view taken along line XIC-XIC shown in FIG. 14E, and FIG. 14D is a cross-sectional view taken along line XID-XID shown in FIG. 14E.

14A and 14B show an intermediate shaft 60 and a clutch 87.
Shows the positional relationship of. Clutch 87 is spring 8
9 (FIG. 13A), it is constantly urged in the direction of arrow 90. In the hammer drill mode, the clutch 87 is located on the intermediate shaft 60 in the state shown in FIG. 14A. That is, the clutch 87 is pressed by the spring 89 in the direction of arrow 90, and the spline 74 of the clutch 87,
75 and the splines 81 and 82 formed on the intermediate shaft 60 mesh with each other, and the clutch 87 rotates as the intermediate shaft 60 rotates.

At one end of the clutch 87, FIG.
As shown in FIG. 5, a clutch pawl 86 is formed, and a reciprocating bearing pawl 85 is formed on the other end of the boss 3. When the clutch 87 is positioned as shown in FIG. 14A, the clutch pawl 86 of the clutch 87 and the reciprocating bearing pawl 85 of the boss 3 are adapted to engage with each other. As a result, the rotation of the intermediate shaft 60 causes the clutch 8 to rotate.
It is transmitted to the boss 3 via 7, and the arm 17 reciprocates to transmit the striking motion to the tool portion.

Since the rotation of the intermediate shaft 60 is always transmitted to the tool portion via the pinion 83 as described above,
When the clutch 87 is located in the state shown in FIG. 4A, it operates in the hammer drill mode.

On the other hand, in the drill mode, the clutch switching lever 88 (FIG. 13A) is rotated. By rotating the clutch switching lever 88, the lever pin 84 moves in the direction of arrow 91.
The lever pin 84 is fitted in the clutch recess 76 formed in the clutch 87, and the clutch 87 compresses the spring 89 by receiving the pressure of the lever pin 84, and the arrow 9
Move in one direction.

By the movement of the clutch 87, the clutch claw 86 and the reciprocating bearing claw 8 formed on the boss 3 are formed.
5, the rotation of the intermediate shaft 60 is not transmitted to the boss 3, and only the rotational movement is transmitted to the tool portion. Thus, the operation in the drill mode is performed.

Incidentally, FIG. 14F shows a working process of the clutch 87. The above-mentioned spline 7 is provided in the clutch 87.
Since it is necessary to form 4, 75, first, the clutch 87
The machining spline 77 is formed over the entire length of the inside, and then the central portion of the machining spline 77 is removed to remove the spline 7.
4 and 75.

[0022]

The above conventional rotary tool has the following problems. First, in the first conventional example shown in FIGS. 11 and 12, the clutch 61 includes the intermediate shaft 6
It is spline-coupled to 0, and is constantly rotating along with the intermediate shaft 60. Then, the head portion 68a of the eccentric pin 68 is fitted in the concave groove 62 of the clutch 61. Therefore, there is a problem in that the clutch 61 that constantly rotates causes the head 68a of the eccentric pin 68 to be worn out and lack durability.

There is also a problem that a friction noise is generated by the contact between the head portion 68a and the concave groove 62 of the clutch 61 which is constantly rotating. Further, the groove 62 of the clutch 61
The eccentric pin 68 may generate heat due to frictional heat between the head 68a and the head 68a, and this heat may be transmitted to the change lever main body 71 and the switching lever formed of resin or the like may be deformed. In addition, the heat generated by the switching lever causes a problem that work safety is reduced.

In the second conventional example, in the hammer drill mode, the clutch 87 receives the pressure of the spring 89 and moves in the direction of the arrow 90 and the lever pin 84.
Is not in contact with the clutch 87. And
In the drill mode, the lever pin 84 presses the clutch 87 to move the clutch 87 in the direction of arrow 91 as shown in FIG. 13A, the engagement between the clutch 87 and the intermediate shaft 60 is released, and the clutch 87 rotates. It becomes a state not to do.

As described above, the lever pin 84 does not come into contact with the rotated clutch 87, and the problem of the first conventional example does not occur. However, this second conventional example is a two-mode switching of a drill mode and a hammer drill mode, and cannot be applied to a mechanism of three-mode switching of a drill mode, a hammer drill mode, and a hammer mode.

Therefore, the present invention can improve the durability of the switching member in the rotary tool capable of switching among the drill mode, the hammer drill mode, and the hammer mode, and further, no friction noise is generated during driving. Another object of the present invention is to provide a rotary tool operation switching mechanism capable of avoiding deformation and heat generation of a resin lever or the like of a switching member due to frictional heat and ensuring work safety.

[0027]

An operation switching mechanism for a rotary tool according to a first aspect of the present invention is attached to an intermediate shaft and an intermediate shaft that rotate by receiving the drive of a drive unit, and moves in the axial direction of the intermediate shaft. As a result, the first transmission member, which is located in the engaged state of rotating with the intermediate shaft or in the released state of being rotatable with respect to the intermediate shaft, is attached to the intermediate shaft,
By moving in the axial direction of the intermediate shaft, the second transmission member and the first transmission member located in the engaged state of rotating with the intermediate shaft or the released state of being rotatable with respect to the intermediate shaft rotate with the first transmitting member. Then, the impact driving member that converts the rotational motion into the impacting motion and transmits the impacting motion to the tool unit rotates with the second transmission member,
A rotation driving member for transmitting the rotational movement to the tool portion, and a switching member for directly or indirectly contacting either the first transmission member or the second transmission member are provided, and the switching member serves as the first transmission member. The first transmission member is directly or indirectly abutted to move from the engaged state to the released state, and the switching member is directly or indirectly abutted to the second transmission member to move the second transmission member. As a result, the engaged state is changed to the released state, and the switching member is not in contact with either the first transmission member or the second transmission member, so that both the first transmission member and the second transmission member are in the engaged state. The feature is that

According to a second aspect of the present invention, there is provided a rotary tool motion switching mechanism according to the first aspect, which is a lock member which is movable in the axial direction of the intermediate shaft and is non-rotatable. A lock member that meshes with the second transmission member at the reference position when the second transmission member switches from the engaged state to the released state; and a biasing member that biases the lock member toward the reference position. It is characterized by that.

An operation switching mechanism for a rotary tool according to a third aspect of the invention is rotated by being driven by a driving unit, is attached to an intermediate shaft having an engaging portion, and is attached to the intermediate shaft, and moves in the axial direction of the intermediate shaft. As a result, the first transmission member located in the engaged state of rotating with the intermediate shaft or in the released state of being rotatable with respect to the intermediate shaft rotates with the first transmitting member, and the rotational motion becomes the striking motion. The impact driving member that is converted and transmitted to the tool portion, the rotation driving member that is positioned in an engaged state that rotates with the engaging portion of the intermediate shaft, or a released state that is rotatable with respect to the engaging portion of the intermediate shaft. And a rotary drive member that transmits a rotary motion to the tool portion when in the engaged state, and a switching member that directly or indirectly abuts either the first transmission member or the rotary drive member, and The switching member is the first transmission unit. Directly or indirectly abutting on the rotary driving member and moving the first transmission member to release the engaged state, and the switching member directly or indirectly abuts the rotary driving member to move the rotary driving member. The engaged state is released from the engaged state, and the switching member is not in contact with either the first transmission member or the rotation driving member, so that both the first transmission member and the rotation driving member are in the engaged state. Is characterized by.

A rotary tool operation switching mechanism according to a fourth aspect is the rotary tool operation switching mechanism according to the third aspect, wherein the rotary drive member is moved in the axial direction of the rotary shaft to be engaged or released. A lock member that is switched to the state, is movable in the axial direction of the rotation drive member, and is not rotatable, and when the rotation drive member is switched from the engaged state to the released state, the rotation drive is performed at the reference position. It is characterized in that a lock member that meshes with the member and a biasing member that biases the lock member toward the reference position are provided.

[0031]

In the operation switching mechanism for the rotary tool according to the first aspect of the present invention, the switching member comes into direct or indirect contact with the first transmission member and is disengaged from the engaged state by moving the first transmission member. State. Further, the switching member comes into direct or indirect contact with the second transmission member, and the second transmission member is moved to change the engaged state to the released state. Then, the switching member does not contact either the first transmission member or the second transmission member, so that both the first transmission member and the second transmission member are brought into the engaged state.

That is, when the first transmission member is brought into the released state by the switching member, only the second transmission member is brought into the engaged state, and the rotational movement is transmitted to the tool portion via the rotation driving member (rotation). Operation function). When the second transmission member is released by the switching member, only the first transmission member is in the engaged state and the striking motion is transmitted to the tool portion via the striking drive member (striking motion function). .

Further, when the switching member does not contact either the first transmission member or the second transmission member, both the first transmission member and the second transmission member are in the engaged state, and the tool portion is rotated respectively. The rotation operation and the impact operation are transmitted to the tool portion via the drive member and the impact drive member (impact rotation operation function).

As described above, by rotating the switching member, it is possible to select the rotation operation function, the impact operation function, or the impact rotation operation function.

When the switching member comes into direct or indirect contact with the first transmission member or the second transmission member, the first transmission member and the second transmission member move to switch from the engaged state to the released state. . That is, the first transmission member and the second transmission member are rotatable with respect to the intermediate shaft and are in a state of not rotating with the intermediate shaft.

Therefore, the durability of the switching member can be improved without abrasion of the switching member that directly or indirectly contacts the first transmission member and the second transmission member. Further, since the first transmission member and the second transmission member are in the non-rotating state, friction noise is not generated during driving due to the contact of the switching member. Further, the switching member does not generate heat due to frictional heat, and for example, the resin lever or the like connected to the switching member is not deformed and does not generate heat, so that work safety can be achieved.

In the mechanism for switching the operation of the rotary tool according to the second aspect, the lock member meshes with the second transmission member at the reference position when the second transmission member is switched from the engaged state to the released state. The lock member cannot rotate. Therefore, it is possible to reliably prevent the tool portion from rotating unexpectedly by stopping and locking the rotation of the second transmission member located in the released state.

Further, the lock member is movable in the axial direction of the intermediate shaft. Therefore, when the rotation angle of the second transmission member deviates from the engagement angle with respect to the lock member,
When the transmission member is switched from the engaged state to the released state, the lock member is pressed by the second transmission member and moves in the axial direction of the intermediate shaft. Therefore, even if the rotation angle of the second transmission member deviates from the meshing angle with respect to the lock member, the switching member can be switched, and the second transmission member can be switched from the engaged state to the released state. You can

Further, the lock member meshes with the second transmission member at the reference position, and the lock member is urged toward the reference position by the urging member. Therefore, the lock member can be always held at the reference position. Further, even when the lock member is pressed and moved due to the shift of the meshing angle of the second transmission member, the lock member immediately returns to the reference position at the time when the shift of the meshing angle is eliminated. Can mesh with.

In the operation switching mechanism of the rotary tool according to the third aspect, the switching member directly or indirectly contacts the first transmission member, and the first transmission member is moved to change the engagement state to the released state. To do. Further, the switching member comes into direct or indirect contact with the rotary drive member, and the rotary drive member is moved to change the engaged state to the released state. Further, since the switching member does not contact either the first transmission member or the rotation driving member, both the first transmission member and the rotation driving member are brought into the engaged state.

That is, when the first transmission member is released by the switching member, only the rotary drive member is brought into the engaged state, and the rotary motion is transmitted to the tool portion (rotary motion function). Further, when the rotation driving member is released by the switching member, only the first transmission member is brought into the engaged state, and the striking motion is transmitted to the tool portion via the striking drive member (striking motion function).

Furthermore, when the switching member does not abut on either the first transmission member or the rotation driving member, both the first transmission member and the rotation driving member are in an engaged state, and the tool portion is rotated and impacted. Is transmitted (percussion rotation operation function).

As described above, by rotating the switching member, it is possible to select the rotation operation function, the impact operation function, or the impact rotation operation function.

When the switching member comes into direct or indirect contact with the first transmission member or the rotation driving member, the first transmission member and the rotation driving member move to switch from the engaged state to the released state. That is, the first transmission member and the rotation driving member are rotatable with respect to the intermediate shaft and the engaging portion of the intermediate shaft, respectively, and are in a state of not rotating with the intermediate shaft and the engaging portion of the intermediate shaft.

Therefore, the durability of the switching member can be improved without abrasion of the switching member that directly or indirectly contacts the first transmission member and the rotation driving member. Further, since the first transmission member and the rotation driving member are in the non-rotating state, the friction noise is not generated by the contact of the switching member. Further, the switching member does not generate heat due to frictional heat, and for example, the resin lever or the like connected to the switching member is not deformed and does not generate heat, so that work safety can be achieved.

In the operation switching mechanism of the rotary tool according to the fourth aspect, the rotary drive member is switched between the engaged state and the released state by moving in the axial direction of the rotary shaft,
The lock member meshes with the rotary drive member at the reference position when the rotary drive member is switched from the engaged state to the released state. The lock member cannot rotate. Therefore, it is possible to reliably prevent the rotation of the rotation driving member located in the released state from being stopped and locked, and the tool portion from rotating unexpectedly.

Further, the lock member is movable in the axial direction of the rotary drive member. Therefore, when the rotation angle of the rotation drive member is deviated from the engagement angle with respect to the lock member and the rotation drive member is switched from the engaged state to the released state, the rotation drive member presses the lock member in the axial direction. Moving. Therefore, even when the rotation angle of the rotary drive member deviates from the meshing angle with respect to the lock member, the switching member can be switched, and the rotary drive member can be switched from the engaged state to the released state. .

Further, the lock member meshes with the rotary drive member at the reference position, and the lock member is biased toward the reference position by the biasing member. Therefore, the lock member can be always held at the reference position. Further, even when the lock member is pressed and moved due to the deviation of the engagement angle of the rotary drive member, the lock member immediately returns to the reference position and meshes with the rotation drive member when the deviation of the engagement angle is resolved. can do.

[0049]

BEST MODE FOR CARRYING OUT THE INVENTION

[First Embodiment] A first embodiment of the operation switching mechanism for a rotary tool according to the present invention will be described with reference to the drawings. FIG. 1 is a side sectional view of the entire hammer drill according to this embodiment. As shown in FIG. 1, the hammer drill is provided with a motor 15 as a drive unit.
The drive of 5 rotates the pinion 16.

The pinion 16 meshes with the gear 9, and the gear 9 is integrally fixed to the intermediate shaft 2. Both ends of the intermediate shaft 2 are supported by bearings and attached to the housing 10.

FIG. 2 is a detailed drawing of the vicinity of the intermediate shaft 2. An intermediate shaft spline portion 2T is formed at the center of the intermediate shaft 2. A second clutch 5 as a second transmission member is attached to the intermediate shaft 2. This second
The clutch 5 is held slidably in the axial direction of the intermediate shaft 2 (directions of arrows 90 and 91).

The second clutch 5 has a second clutch engaging portion 5
M (see FIG. 2B) is formed, and the second clutch engaging portion 5M can engage with the intermediate shaft spline portion 2T formed on the intermediate shaft 2. When the second clutch engagement portion 5M is engaged with the intermediate shaft spline portion 2T (engagement state), the second
The clutch 5 rotates as the intermediate shaft 2 rotates.

On the other hand, the second clutch 5 has an arrow 91.
When the second clutch engagement portion 5M and the intermediate shaft spline portion 2T are disengaged (disengaged state) by moving in the direction, the second clutch 5 becomes rotatable with respect to the intermediate shaft 2. The second clutch 5 is constantly urged by the spring 12 in the direction of arrow 90.

The second clutch 5 has a second clutch gear portion 5G. As shown in FIG. 1, the second clutch gear portion 5G meshes with a final gear 6 as a rotation driving member. The arrow 90 of the second clutch 5,
The second clutch gear portion 5 regardless of the movement in the 91-direction.
The meshing relationship between G and the final gear 6 is always maintained, and the second gear
It rotates with the clutch 5.

The final gear 6 is attached to the tool holder 25. The final gear 6 and the tool holder 25 are connected by a clutch mechanism by the elastic force of the disc spring 19. The disc spring 19 is a washer 21,
It is attached by a snap ring 20 and adds resilience to the final gear 6.

The second clutch 5 moves in the direction of arrow 90,
When engaged with the intermediate shaft spline portion 2T of the intermediate shaft 2 (FIG. 2A), the second clutch 5 rotates along with the intermediate shaft 2, and in response to this, the final gear 6 also rotates. Then, according to the final gear 6, the tool holder 25
Rotates, and the bit 24, which is the tool portion, performs a rotating operation.

When a constant load is applied to the bit 24 during the work, the clutch mechanism between the final gear 6 and the tool holder 25 is disengaged against the resilience of the disc spring 19, and the bit 24
The rotation is not transmitted to. As a result, the work is safe and the load on the motor 15 is avoided.

A locking gear 13 as a locking member is fixed to the housing 10 by a bolt 14. The locking gear 13 engages with the locking spline portion 5K (see FIG. 2B) of the second clutch 5 when the second clutch 5 moves in the direction of arrow 91 and is in the released state, and the second clutch 5 Is locked so that it cannot rotate.

The intermediate shaft 2 has a boss 3 as a striking drive member.
Is rotatably mounted. The boss 3 is provided with an arm 17, and when the boss 3 rotates, this rotation operation is reciprocated in the directions of arrows 90 and 91 (striking operation).
And is transmitted to the piston cylinder 18. The reciprocating motion of the piston cylinder 18 is transmitted to the bit 24 via the first hammer 22 and the second hammer 23, and the bit 24 performs a striking operation.

The intermediate shaft 2 has a first transmission member, which is a first transmission member.
The clutch 4 is rotatably attached. This first
Similarly to the second clutch 5, the clutch 4 is also formed with a first clutch engaging portion 4M (see FIG. 2C), which is indicated by an arrow 91.
When it moves in the direction, it engages with the intermediate shaft spline portion 2T formed on the intermediate shaft 2. When the first clutch engagement portion 4M engages with the intermediate shaft spline portion 2T (engagement state), the first clutch 4 rotates as the intermediate shaft 2 rotates.

On the other hand, the first clutch 4 has the arrow 90.
When the first clutch engaging portion 4M is disengaged from the intermediate shaft spline portion 2T (released state) by moving in the direction, the first clutch 4 becomes rotatable with respect to the intermediate shaft 2. A spring 11 is provided between the boss 3 and the first clutch 4.
Is provided, and the first clutch 4 is constantly urged in the direction of arrow 91.

As shown in FIG. 2A, the boss 3 is formed with a boss engaging portion 3G, while the first clutch 4 is provided with a first clutch spline portion 4G which is splined to the boss engaging portion 3G. Has been formed. Regardless of the movement of the first clutch 4 in the directions of the arrows 90 and 91, the first clutch spline portion 4G and the boss engagement portion 3G always maintain the coupling relationship, and the boss 3 rotates with the first clutch 4. It is like this.

As shown in FIG. 2, a pin 7 which is a switching member is provided near the lower portion of the intermediate shaft spline portion 2T of the intermediate shaft 2.
Is located. The pin 7 is fixed to the switching lever 8, and the switching lever 8 projects outside the housing 10 (FIG. 1). The switching lever 8 can be rotated from the outside. The switching lever 8 and the pin 7 are omitted in FIG.

Details of the switching lever 8 and the pin 7 are shown in FIG. FIG. 3A is a plan view, and FIG. 3B is II shown in FIG. 2A.
It is a sectional view taken along the arrow IB. As shown in FIG. 3A, the pin 7 is fixed at an eccentric position with respect to the rotation center of the switching lever 8, and by rotating the switching lever 8, the pin 7 is moved to positions P1, P2, or P3.

Further, as shown in FIG. 3B, when the pin 7 is moved to the position P2, the flange portion 4F of the first clutch 4 is
It comes into contact with. The pin 7 is located at the position P3.
Similarly, the pin 7 comes into contact with the flange portion 5F of the second clutch 5 when it is moved to (not shown).

Next, the mode switching operation in this embodiment will be described. FIG. 2A shows the state of the hammer drill mode. In this case, the switching lever 8 is shown in FIG.
It is located at the position P1 shown in FIG. At this time, the pin 7 is positioned so as not to contact either the first clutch 4 or the second clutch 5. Since the pin 7 does not contact the first clutch 4 and the second clutch 5, the first clutch 4 and the second clutch 5 have the spring 11 and the second clutch 5, respectively.
It is biased by 12 and engages with the intermediate shaft spline portion 2T formed on the intermediate shaft 2 (engaged state).

As a result, both the first clutch 4 and the second clutch 5 rotate with the rotation of the intermediate shaft 2. That is, by the rotation of the second clutch 5, the rotary motion is transmitted to the bit 24 via the final gear 6 and the tool holder 25. Further, by the rotation of the first clutch 4, a striking motion of reciprocating in the axial direction is transmitted to the bit 24 via the boss 3 and the arm 17. Thus, the bit 24 operates in a hammer drill mode in which it strikes while rotating.

FIG. 2B shows the state of the hammer mode. When switching to hammer mode, switch lever 8
Is rotated to move the pin 7 from the positions P1 to P2 shown in FIG. 3A.
Move to As a result, as shown in FIG. 2B, the pin 7 presses the flange portion 5F of the second clutch 5 in the direction of arrow 91, and the second clutch 5 moves against the elastic force of the spring 12.

Then, the second clutch engaging portion 5M of the second clutch 5 and the intermediate shaft spline portion 2T of the intermediate shaft 2 are disengaged, and the second clutch 5 is rotatable with respect to the intermediate shaft 2. In this state, that is, in the free state in which the intermediate shaft 2 does not rotate. Since the second clutch 5 is in the free state, the rotary motion is not transmitted to the bit 24. In this case,
As in the case of FIG. 2A, the first clutch 4 has the first clutch engaging portion 4M engaged with the intermediate shaft spline portion 2T, so that the impact motion is transmitted to the bit 24 and the hammer operates in the hammer mode.

As shown in FIG. 2B, when the second clutch 5 moves in the direction of arrow 91, the locking spline portion 5K formed on the outer periphery of the flange portion 5F of the second clutch 5
Engages with the lock gear 13 shown in FIG. 1 and becomes a non-rotatable locked state. As a result, it is possible to prevent the bit 24 from unintentionally rotating during the operation in the hammer mode, and it is possible to improve work safety.

In the hammer mode, the hammer mode bit 24 is attached, but it may be desired to manually adjust the angle of the bit 24. In this case, the switching lever 8 is rotationally operated to position the pin 7 on the range H1 between the positions P1 and P2 (chisel-free mode).

As a result, the second clutch 5 is positioned in the middle between the state shown in FIG. 2A and the state shown in FIG. 2B. That is, the second clutch 5 is disengaged from the intermediate shaft spline portion 2T of the intermediate shaft 2, and the locking spline portion 5K is released.
Is not engaged with the lock gear 13. Then, the angle of the bit 24 can be easily manually adjusted without receiving a load on the intermediate shaft 2.

FIG. 2C shows the state of the drill mode. When switching to drill mode, switching lever 8
Is rotated to move the pin 7 from the position P1 shown in FIG. 3A to the position P3. As a result, as shown in FIG. 2C, the pin 7 presses the flange portion 4F of the first clutch 4 in the direction of arrow 90, and the first clutch 4 moves against the elastic force of the spring 11.

Then, the engagement between the first clutch engaging portion 4M of the first clutch 4 and the intermediate shaft spline portion 2T of the intermediate shaft 2 is released, and the first clutch 4 is rotatable with respect to the intermediate shaft 2. That is, the intermediate shaft 2 is brought into a free state in which it does not rotate. Since the first clutch 4 is in the free state, the striking motion is not transmitted to the bit 24. In this case, the second clutch 5 is engaged with the intermediate shaft spline portion 2T of the intermediate shaft 2 as in the case of FIGS. 2A and 2B, so that the bit 24 is rotated. Is transmitted to operate as a drill mode.

As described above, the mode is switched by rotating the switching lever 8 and moving the position of the pin 7. Here, in the hammer drill mode shown in FIG. 2A, the pin 7 does not contact either the first clutch 4 or the second clutch 5.

In the hammer mode shown in FIG. 2B,
The pin 7 contacts the second clutch 5, but the second clutch 5
Is in a state where it is disengaged from the intermediate shaft spline portion 2T of the intermediate shaft 2 and therefore is in a state where it does not rotate. In the drill mode shown in FIG. 2C, the pin 7 contacts the first clutch 4, but in this case as well, the first clutch 4 is in a state where the engagement with the intermediate shaft spline portion 2T of the intermediate shaft 2 is released. Because it is not rotating.

As described above, the pin 7 does not come into contact with the rotating first clutch 4 and second clutch 5 in any mode, and the durability of the pin 7 can be improved without being worn by the rotational contact. . Friction noise between the rotating first clutch 4 and second clutch 5 and the pin 7 is not generated. Further, since the pin 7 does not generate heat due to frictional heat, the switching lever 8 does not receive heat and is not deformed, and work safety can be achieved.

The first clutch 4 and the second clutch 5 in this embodiment have the shapes shown in FIGS. Therefore, in the process of processing the first clutch 4 and the second clutch 5, it is not necessary to remove the central portion of the processing spline on the inner circumference unlike the conventional clutch 87 shown in FIG. 14F, and the inner diameter L1 (Fig. 14
The dimensional control of E) is not difficult.

In the present embodiment, the pin 7 directly contacts the first clutch 4 and the second clutch 5 to move them, but the pin 7 indirectly contacts and moves with another member interposed. May be.

[Second Embodiment] Next, a second embodiment of the operation switching mechanism for a rotary tool according to the present invention will be described with reference to FIGS. 4 to 6. FIG. 4 is a side sectional view of the entire hammer drill according to the present embodiment, and FIG.
6A, 6B, 6C, and 6C are sectional views taken along line VI-VI in FIG.

Also in the present embodiment, as in the first embodiment, a lock spline portion 5K is formed on the outer periphery of the flange portion 5F of the second clutch 5. Further, in the present embodiment, a lock plate 50 is provided instead of the lock gear 13 shown in the first embodiment (see FIGS. 5 and 6). The lock plate 50 is formed with a groove portion 50K that meshes with the lock spline portion 5K of the flange portion 5F of the second clutch 5.

As shown in FIG. 5, two bolts 51 and 52 penetrate the lock plate 50, and the lock plate 50 is supported by the two bolts 51 and 52 so that it cannot rotate. The bolts 51 and 52 are fixed to the housing 10 (see FIG. 6).

The lock plate 50 is provided so as to be movable in the directions of arrows 90 and 91 along the bolts 51 and 52. A compression coil spring 53 (FIG. 6) is attached to the bolt 51, and the lock plate 50 is always attached with an arrow 90.
Biased in the direction. In the present embodiment, the bolt 51
Although the compression coil spring 53 is attached only to the bolt, the compression coil spring may be attached to the bolt 52.

As described in the first embodiment, when switching to the hammer mode, the switching lever 8 is rotated to move the pin 7 from the position P1 shown in FIG. 3A to P2. As a result, the pin 7 presses the flange portion 5F of the second clutch 5 in the direction of arrow 91, and the second clutch 5 moves against the elastic force of the spring 12 (see FIG. 4).

When the second clutch 5 moves in the direction of arrow 91, the lock spline portion 5K formed on the outer periphery of the flange portion 5F of the second clutch 5 is locked by the lock plate 50.
Mesh with the groove portion 50K (see FIG. 6C). The meshing of the two causes the second clutch 5 to be in a locked state in which it cannot rotate.

As a result, it is possible to reliably prevent the bit 24 from unintentionally rotating during the operation in the hammer mode, and it is possible to secure work safety. The position of the lock plate 50 shown in FIGS. 6A and 6C (the position of the lock plate 50 that can mesh with the second clutch 5) is the reference position of the lock plate 50 in the present embodiment.

By the way, the rotation angle of the second clutch 5 about the intermediate shaft 2 is determined by the groove 50K of the lock plate 50.
May be deviated from the meshing angle with respect to. When the lock plate 50 and the lock plate 50 are not smoothly meshed with each other and the lock plate 50 is fixed at the reference position shown in FIG.
It is blocked by 0 and cannot move in the direction of arrow 91.

In this embodiment, the lock plate 50 is movable in the direction of arrow 91 along the bolts 51 and 52.
Therefore, even when the rotation angle of the second clutch 5 is deviated from the meshing angle of the lock plate 50 with respect to the groove portion 50K, the compression coil spring 53 as shown in FIG. 6B.
Is compressed, and the lock plate 50 allows the second clutch 5 to move.

Since the through hole formed in the lock plate 50 is formed to be slightly larger than the bolts 51 and 52, the bolts 51 and 52 are moved by the movement of the second clutch 5 as shown in FIG. 6B. Can be located at an angle to.

Further, since the lock plate 50 is constantly urged in the direction of arrow 90 by the compression coil spring 53, the lock plate 50 immediately returns to the reference position when the deviation of the meshing angle is eliminated, and the second clutch 5 is released. Can mesh with. For example, from the state shown in FIG. 6B,
When the second clutch 5 slightly rotates due to the influence of the rotation of the intermediate shaft 2 or vibration, the lock plate 50 is immediately biased by the compression coil spring 53 and immediately returns to the reference position shown in FIG. Mesh.

Other configurations of the hammer drill in this embodiment are the same as those in the first embodiment.

[Third Embodiment] Next, a third embodiment of the operation switching mechanism for a rotary tool according to the present invention will be described with reference to FIGS. Similar to the first embodiment, the intermediate shaft 2 is provided with the first clutch 4 and the boss 3. Then, the first clutch 4 is rotated by engaging with the intermediate shaft spline portion 2T, whereby the arm 17 transmits the striking motion to the bit 24.

In this embodiment, the intermediate shaft gear 30 is integrally formed with the intermediate shaft 2. Then, the final gear 6 (rotational drive member) meshes with the intermediate shaft gear 30. As shown in FIG. 7, a steel ball 32 and a spring 33 are provided at the tip of the intermediate shaft 2 to prevent the intermediate shaft 2 from rattling. In addition,
A bearing may be provided at the tip of the intermediate shaft 2 as in the first embodiment, and the steel ball 32 and the spring 33 in the present embodiment may be provided in the first embodiment.

A tool holder spline portion 42 is formed on the tool holder 25, and a gear holder 36 is formed there.
The gear holder spline section 40 is coupled to hold the gear holder 36 slidably in the directions of arrows 90 and 91. The final gear 6 is rotatably provided on the gear holder 36 with the friction plate 35 interposed therebetween. The gear holder 36 is further provided with a nut 39 via a disc spring 37, and the final gear 6 rotates integrally due to friction with the gear holder 36. In addition, the nut 39
A brake plate 31 is embedded in the. The gear holder 36 is biased by the spring 34 in the direction of arrow 90.

The details of the braking plate 31 are shown in FIG. The braking plate 31 has a hole 45, which is shown in FIG. 10B.
The support shaft 46 shown in FIG. The support shaft 46 is fixed in the housing 10, and the braking plate 31 is movable along the support shaft 46 in the directions of arrows 90 and 91. The support shaft 46 is not shown in FIGS. 7 to 9.

In this embodiment, the switching lever 43 is attached to the side surface of the housing 10. The switching lever 43 is provided with two first pins 43a and two second pins 43b. This first pin 43a, the second
The pin 43b is a switching member in this embodiment,
Both are provided side by side on a line passing through the rotation center of the switching lever 43 (FIGS. 7 to 10).

As shown in FIG. 10, the first pin 43a is longer than the second pin 43b and is located near the center of the switching lever 43. When the switching lever 43 is rotated, as shown in FIG. 8, the second pin 43b
Contacts the protruding piece 47 of the braking plate 31, and presses the braking plate 31 in the direction of arrow 91.

When the switching lever 43 is rotated from the position shown in FIG. 7 to the position shown in FIG. 9, the first pin 4
3a contacts the first clutch 4 and presses the first clutch 4 in the direction of arrow 90. In this case, the second pin 43b is the first
Since it is shorter than the pin 43a, it does not contact the first clutch 4.

As described above, the first pins 43a having different lengths,
By providing the second pin 43b at different positions apart from the center of rotation of the switching lever 43, the moving lengths of the braking plate 31 and the first clutch 4 can be controlled. The other mechanism in this embodiment is the same as that in the first embodiment.

Next, the mode switching operation in this embodiment will be described below. FIG. 7 shows the state of the hammer drill mode. In this case, the first clutch 4 is engaged with the intermediate shaft spline portion 2T of the intermediate shaft 2 (engaged state), and the striking motion is transmitted to the bit 24 via the boss 3 and the arm 17. Further, the final gear 6 meshes with the intermediate shaft gear 30 (engaged state), and the rotary motion is transmitted to the bit 24 via the tool holder 25. Thus, the bit 24 operates in a hammer drill mode in which it strikes while rotating.

FIG. 8 shows the state of the hammer mode. When switching to the hammer mode, the switching lever 43 is rotated clockwise from the state shown in FIG. 7 to the position shown in FIG. As a result, the second pin 43b presses the braking plate 31 in the arrow 91 direction, and accordingly, the entire gear holder 36 supporting the final gear 6 moves in the arrow 91 direction against the elastic force of the spring 34.

As a result, the engagement between the final gear 6 and the intermediate shaft gear 30 is released (released state), the rotary motion is not transmitted to the bit 24, and the bit 24 only performs the striking motion. Take action. In this case, the final gear 6 meshes with the locking gear 41 serving as a locking member, and becomes a non-rotatable locked state. As a result, it is possible to prevent the bit 24 from unintentionally rotating during the operation in the hammer mode, and it is possible to improve work safety.

FIG. 9 shows the state of the drill mode.
When switching to the drill mode, the switching lever 43 is rotated counterclockwise from the state shown in FIG. 7 to the position shown in FIG. As a result, the first pin 43a has the first
The clutch 4 is pressed, and the first clutch 4 is pressed accordingly.
Moves in the direction of arrow 90 against the elastic force of the spring 11.

By the movement of the first clutch 4, the engagement between the intermediate shaft spline portion 2T of the intermediate shaft 2 and the first clutch 4 is released (disengaged state), and the rotational operation of the intermediate shaft 2 is bit 2.
4 is not transmitted as a striking motion, the bit 24 only performs a rotating motion, and operates in a drill mode.

The final gear 6 is disengaged from the intermediate shaft gear 30 and the locking gear 41 is set by positioning the rotation angle of the switching lever 43 between the state shown in FIG. 7 and the state shown in FIG. The position of the bit 24 can be manually adjusted by positioning it in a non-meshing state (chisel-free mode).

As described above, the mode switching is performed by rotating the switching lever 43 and moving the positions of the first pin 43a and the second pin 43b. here,
In the hammer drill mode shown in FIG. 7, the first pin 43a and the second pin 43b are the braking plate 31 and the first clutch 4.
Does not come into contact with either.

In the hammer mode shown in FIG. 8, the second pin 43b contacts the braking plate 31, but the final gear 6 does not rotate because it is disengaged from the intermediate shaft gear 30 of the intermediate shaft 2. It is in a state. Further, in the drill mode shown in FIG. 9, the first pin 43a is connected to the first clutch 4
However, in this case as well, the first clutch 4 is in a state of not rotating because it is disengaged from the intermediate shaft spline portion 2T of the intermediate shaft 2.

In this way, the first pin 43a and the second pin 4
Since 3b is in contact with the brake plate 31 that does not rotate, it does not wear due to rotational contact, and durability can be improved. In addition, the first pin 43a, the second pin 43b and the braking plate 3
The frictional noise with 1 does not occur. Further, since the first pin 43a and the second pin 43b do not generate heat due to frictional heat, the switching lever 43 does not receive heat and is not deformed, and work safety can be achieved.

In the present embodiment, the first pin 43a is brought into direct contact with the first clutch 4 and moved, but it may be indirectly brought into contact with another member via an intervening member. Further, the second pin 43b indirectly contacts the final gear 6 through the braking plate 31 and the like, and is moved,
You may make it contact | abut directly to the final gear 6.

[Fourth Embodiment] Next, a fourth embodiment of the operation switching mechanism for the rotary tool according to the present invention will be described. In this embodiment, the lock plate 50 shown in the second embodiment is applied to the hammer drill shown in the third embodiment. That is, the lock plate 50 (FIGS. 5 and 6) is provided (not shown) instead of the locking gear 41 (FIGS. 7 to 9) of the third embodiment. A gear groove portion that meshes with the final gear 6 is formed in the lock plate 50.

The lock plate 50 is supported by the bolts 51 and 52, and the compression coil spring 53 attached to the bolt 51 urges the lock plate 50 in the direction of arrow 90 (see FIGS. 5 and 6). Accordingly, even when the rotation angle of the final gear 6 is deviated from the meshing angle of the lock plate 50 with respect to the gear groove portion,
The compression coil spring 53 is compressed, and the lock plate 50 allows the second clutch 5 to move (see FIG. 6B).

Further, since the lock plate 50 is constantly urged in the direction of the arrow 90 by the compression coil spring 53, the lock plate 50 immediately returns to the reference position and the final gear 6 is reached when the deviation of the meshing angle is eliminated. Can mesh. For example, when the final gear 6 slightly rotates from the state shown in FIG. 6B due to the influence of the rotation of the intermediate shaft 2, vibration, etc., the lock plate 50 is immediately biased by the compression coil spring 53 and immediately returns to the reference position. It meshes with the gear 6 (see FIG. 6C).

Other configurations of the hammer drill in this embodiment are the same as those in the third embodiment.

[Other Embodiments] The operation switching mechanism of the rotary tool according to the present invention is not limited to the above embodiments. That is, the switching member comes into contact with the first transmission member directly or indirectly, and moves the first transmission member to bring the engaged state into the released state, and the switching member directly or indirectly contacts the second transmission member. The first transmission member and the second transmission member are brought into contact with each other to move from the engaged state to the released state, and the switching member does not come into contact with either the first transmission member or the second transmission member. Other configurations may be adopted as long as both the transmission members are in the engaged state.

Further, it is movable in the axial direction of the intermediate shaft,
The non-rotatable lock member meshes with the second transmission member at the reference position when the second transmission member is switched from the engaged state to the released state, and the biasing member applies the lock member toward the reference position. Other configurations can be adopted as long as they are active.

Further, the switching member is brought into contact with the first transmission member directly or indirectly and is moved from the engagement state to the released state by moving the first transmission member, and the switching member is directly or indirectly connected to the rotary drive member. The contact state is brought into contact with the rotary drive member by moving the rotary drive member, and the switching member does not come into contact with either the first transfer member or the rotary drive member. Other configurations may be adopted as long as both are in the engaged state.

Further, it is movable in the axial direction of the intermediate shaft,
When the rotation drive member is switched from the engaged state to the released state, the non-rotatable lock member meshes with the rotation drive member at the reference position, and the biasing member biases the lock member toward the reference position. Other configurations can be adopted as long as they are used.

[Brief description of drawings]

FIG. 1 is an overall side sectional view of a hammer drill showing a first embodiment of a rotary tool operation switching mechanism according to the present invention.

2 is a detailed view of the vicinity of the intermediate shaft shown in FIG. 1, where A is a hammer drill mode, B is a hammer mode, and C is a drill mode.

FIG. 3 is a diagram showing details of a switching lever shown in FIG.

FIG. 4 is a side sectional view of a hammer drill showing a second embodiment of the operation switching mechanism of the rotary tool according to the present invention.

5 is a cross-sectional view taken along the line VV shown in FIG.

6 is a sectional view taken along line VI-VI shown in FIG.

FIG. 7 is a side sectional view of a hammer drill showing a third embodiment of the operation switching mechanism of the rotary tool according to the present invention,
The hammer drill mode is shown.

FIG. 8 is a side sectional view of a hammer drill showing a third embodiment of the operation switching mechanism of the rotary tool according to the present invention,
The hammer mode is shown.

FIG. 9 is a side sectional view of a hammer drill showing a third embodiment of the operation switching mechanism of the rotary tool according to the present invention,
Shows the drill mode.

FIG. 10 is a diagram showing details of the vicinity of the braking plate shown in FIGS. 7 to 9;

FIG. 11 is a diagram showing a first conventional example, where A is a drill mode, B is a hammer drill mode, and C is a hammer mode.

FIG. 12 is a diagram showing a clutch moving mechanism in the first conventional example shown in FIG. 11.

FIG. 13 is a diagram showing a second conventional example.

FIG. 14 is a diagram showing details of the clutch shown in FIG.

[Explanation of symbols]

 2 ... Intermediate shaft 3 ... Boss 4 ... First clutch 5 ... Second clutch 6 ... Final gear 7 ... Pin 8, 43-switching lever 13, 41-locking gear 15-motor 17-arm 31-braking plate 43a-first pin 43b ... Second pin 50 ... Lock plate 53 ... Compression coil spring

Claims (4)

[Claims] 1. An intermediate shaft which is rotated by the drive of a drive unit, and an engaged state which is attached to the intermediate shaft and rotates along with the intermediate shaft by moving in the axial direction of the intermediate shaft, or an intermediate shaft. A first transmission member that is located in a released state that is rotatable with respect to the intermediate shaft, and is attached to the intermediate shaft, and is engaged with the intermediate shaft by rotating in the axial direction of the intermediate shaft, or the intermediate shaft. A second transmission member that is rotatable with respect to the second transmission member, and a second transmission member that rotates with the first transmission member and that converts the rotational motion into a striking motion and transmits the striking motion to the tool portion; A rotary drive member that rotates with the rotation of the tool part and that transmits the rotary motion to the tool portion; and a switching member that directly or indirectly contacts either the first transmission member or the second transmission member. Direct to the first transmission member The first transfer member is brought into contact with or indirectly contacted with the first transfer member to move from the engaged state to the released state, and the switching member directly or indirectly contacts the second transfer member to move the second transfer member. As a result, the engaged state is changed to the released state, and the switching member does not contact either the first transmission member or the second transmission member, so that both the first transmission member and the second transmission member are brought into the engaged state. The operation switching mechanism of the rotary tool characterized by the following. 2. A rotary tool operation switching mechanism according to claim 1, wherein the lock member is movable in the axial direction of the intermediate shaft and is not rotatable, and the second transmission member is in an engaged state. An operation switching mechanism for a rotary tool, comprising: a lock member that meshes with the second transmission member at the reference position when the release state is switched, and a biasing member that biases the lock member toward the reference position. . 3. An intermediate shaft which is driven by a drive unit to rotate, and which is attached to an intermediate shaft having an engaging portion and an intermediate shaft, and which rotates with the intermediate shaft by moving in the axial direction of the intermediate shaft. The first transmission member located in the combined state or in the released state in which it is rotatable with respect to the intermediate shaft, and the impact driving member that rotates with the first transmission member and converts the rotational motion into the impact motion and transmits it to the tool part. A rotary drive member located in an engaged state of rotating with the engaging portion of the intermediate shaft or in a released state of being rotatable with respect to the engaging portion of the intermediate shaft, the tool being driven when in the engaged state. And a switching member that directly or indirectly abuts either the first transmission member or the rotation driving member, and the switching member directly or indirectly contacts the first transmission member. Abutting indirectly, the first transmission The material is moved to change from the engaged state to the released state, the switching member directly or indirectly contacts the rotation driving member, and the rotation driving member is moved to change the engagement state to the released state. However, the first transmission member and the rotation driving member are both brought into an engaged state by not abutting against either the first transmission member or the rotation driving member. 4. The operation switching mechanism for a rotary tool according to claim 3, wherein the rotary drive member is switched between an engaged state and a released state by moving in the axial direction of the rotary shaft, and the rotary drive member shaft is rotated. A lock member that is movable in the direction and that cannot rotate, and that is a lock member that meshes with the rotation drive member at the reference position when the rotation drive member switches from the engaged state to the released state An operation switching mechanism for a rotary tool, comprising: an urging member that urges toward a position.