JP5203129B2 - Rotating tool - Google Patents

Description

  The present invention relates to a rotary tool that outputs rotational power such as a screw tightener called a screw driver, for example.

A screw driver 1 having a conventional clutch mechanism C0 is shown in FIG. The screw driver 1 uses an electric motor 3 (only the output shaft 3a is shown in FIG. 2) built in the main body case 2 as a drive source, and thereby a drive gear 4 and a spindle 5 that rotate. A clutch mechanism C0 is provided therebetween. The electric motor 3 is started by pulling a trigger switch lever (not shown) with a fingertip. The drive gear 4 is rotatably supported via the intermediate shaft 6 and the thrust bearing 13. The intermediate shaft 6 is supported by the main body case 2 via a bearing 7 so as to be rotatable and displaceable in the axial direction.
Clutch teeth 4 a to 4 a and 5 a to 5 a that mesh with each other are provided on the mutually facing surfaces of the drive gear 4 and the spindle 5. The spindle 5 is supported by the main body case 2 via the intermediate shaft 6 and the bearing 8 so as to be displaceable in the axial direction and rotatable about the axis. A bit 9 is attached to the tip of the spindle 5. A compression spring 10 is interposed between the intermediate shaft 6 and the spindle 5. The spindle 5 is urged by the compression spring 10 in a direction to disconnect the clutch mechanism C0 (power cutoff side, right side in FIG. 2).
In addition, the drive gear 4 supports an engagement pin that can be tilted in the rotation direction at a circumferentially divided position. Immediately before the clutch teeth 4a to 4a and 5a to 5a are engaged with each other, the clutch teeth 5a to 5a on the spindle 5 side are engaged with the tip end portions of the engagement pins, whereby each engagement pin is tilted rearward in the rotation direction. When the engaging pin is tilted, the rear end of the engaging pin protrudes from the rear surface of the driving gear 4 and is abutted against the thrust bearing 13, so that the driving gear 4 is displaced integrally with the intermediate shaft 6 toward the axial front side against the compression spring 10. To do. Thus, when the drive gear 4 moves forward, the clutch teeth 4a to 4a and the clutch teeth 5a to 5a of the sleeve 5 are instantaneously engaged with each other, and rotational power is transmitted.
When a screw (not shown) is set at the tip of the bit 9 and the electric motor 3 is activated, when the screw driver 1 is pressed toward the screw fastening material, the spindle 5 is relatively retracted and its clutch teeth 5a to 5a engage with the tips of the engagement pins 12 to 12, whereby the engagement pins 12 to 12 tilt and the drive gear 4 moves forward in the axial direction. As a result, the clutch teeth 4a to 4a and the clutch teeth 5a to 5a are instantaneously engaged with each other and the clutch mechanism C0 is connected. When the clutch mechanism C0 is connected, the rotational power from the electric motor 3 is transmitted to the spindle 5 and screwed.

As the screw tightening progresses, the tip of the stopper sleeve 14 comes into contact with the screw tightening material, and then the screw tightening proceeds further so that the spindle 5 moves forward by the urging force of the compression spring 10. When the screw tightening is completed, the clutch teeth 5a to 5a are disengaged from the distal ends of the engagement pins 12 to 12, so that the drive gear 4 moves backward while the engagement pins 12 to 12 are upright by the action of the compression spring 10. As a result of the drive gear 4 retreating, the engagement between the clutch teeth 4a to 4a and the clutch teeth 5a to 5a of the spindle 5 is instantaneously released, and the clutch mechanism C0 is disconnected. When the clutch mechanism C0 is disconnected, the rotational power of the electric motor 3 is not transmitted to the spindle 5. Further, since the drive gear 4 moves backward, an appropriate gap is generated between the clutch teeth 4a and 5a, so that the drive gear 4 idles. In this way, the engagement of the engagement pins 12 to 12 provided on the drive gear 4 causes the drive gear 4 itself to advance and retreat in the axial direction, so that the clutch mechanism C0 is engaged and disconnected instantaneously. The drive gear 4 is idled without causing any interference between teeth. Therefore, the clutch mechanism C0 constitutes a so-called silent clutch.
When the pressing operation of the screw driver 1 is released after the screw tightening is completed, the tip of the stopper sleeve 14 is separated from the screw tightening material, and the spindle 5 is returned to the forward end position by the biasing force of the compression spring 10.
Usually, in this type of clutch mechanism C0, the drive gear 4 is in the stage where the clutch teeth 5a to 5a of the spindle 5 are engaged with the engagement pins 12 to 12 and the clutch teeth 4a to 4a and 5a to 5a are engaged with each other. On the other hand, a synchro mechanism for smoothly meshing with the spindle 5 rotating in synchronization is employed. In the above configuration, the intermediate shaft 6 is rotatably supported by the body case 2, and the urging force of the compression spring 10 interposed between the intermediate shaft 6 and the spindle 5 is applied to the drive gear 4 and the spindle 5. The spindle 5 is idled (synchronized) immediately before the clutch mechanism C0 is engaged.
On the other hand, it is necessary to prevent the spindle 5 from slipping (so-called co-rotation) when not necessary for the convenience of setting the screw for the bit 9 or the like. For this purpose, a brake member 11 is attached to the main body case 2. As shown in the drawing, when the spindle 5 is returned to the rotational power cutoff position by the compression spring 10, the idling of the flange 5 b of the spindle 5 is pressed against the brake member 11 by the urging force of the compression spring 10, thereby preventing idling. It has become so.
When the spindle 5 is relatively retracted by starting the electric motor 3 and pressing the screw driver 1 in the screw tightening direction, the flange portion 5b is separated from the brake member 11 and there is no rotational resistance. It starts to rotate in synchronism with the drive gear 4 by the friction in the rotational direction due to the urging force. As the spindle 5 rotates in synchronization with the clutch mechanism C0, the engagement of the clutch teeth 5a to 5a with the engagement pins 12 to 12 and the meshing operation of the clutch teeth 4a to 4a and 5a to 5a are performed smoothly. Therefore, the silence and durability of the clutch mechanism C0 and thus the screw driver 1 can be improved.
JP 2005-66782 A Japanese Patent No. 3071523

However, according to the above-described conventional clutch mechanism C0, since it is configured to perform the synchronous rotation using the urging force of the compression spring 10 as described above, the clutch gears 4a to 4a and 5a to 5a are not engaged with each other. Even in the idling state (rotation power cut-off state), the urging force of the compression spring 10 acts on the drive gear 4 via the intermediate shaft 6 and also acts on the spindle 5, and as a result, between the drive gear 4 and the intermediate shaft 6. Friction heat caused by sliding in the rotational direction between the intermediate shaft 6 and the compression spring 10, between the compression spring 10 and the bottom of the support hole 5c, and between the intermediate shaft 6 and the inner peripheral surface of the support hole 5c. This occurred, and there was a problem that the durability of the clutch mechanism C0 was lowered.
Therefore, an object of the present invention is to increase the durability of the clutch mechanism by suppressing the generation of frictional heat between the spindle and the intermediate shaft.

For this reason, this invention was set as the rotary tool of the structure described in each claim of a claim.
According to the rotary tool of the first aspect, when the spindle is moved backward by pushing in the screw tightening direction, the clutch mechanism is connected, and the rotational power of the electric motor is transmitted to the spindle through the drive gear to be tightened. The When the pressing operation of the rotary tool is released, the spindle moves forward and the clutch mechanism is cut off, so that transmission of rotational power to the spindle is cut off.
The drive gear is rotatably supported via an intermediate shaft, and the spindle is supported by the intermediate shaft so as to be rotatable and axially displaceable via an intermediate sleeve. This intermediate shaft does not rotate. For this reason, even if the drive gear rotates (idle), the intermediate shaft does not rotate (so-called co-rotation) by the rotational power, so there is a gap between the intermediate shaft and the intermediate sleeve and between the intermediate sleeve and the compression spring. No frictional heat due to sliding in the rotational direction is generated between the compression spring and the spindle, and therefore the frictional heat generation is suppressed as compared with the conventional one, and the durability of the clutch mechanism and thus the rotary tool is improved. Can do.
Further, since the rotational torque around the spindle is not transmitted to the spindle when the drive gear is idling, the conventional brake member can be omitted.
According to the rotary tool of claim 2, when the spindle is retracted, the spindle is idled (synchronized rotation) by the rotational power of the drive gear via the friction of the synchro member between the spindle and the drive gear, and thereby the clutch The mechanism meshes smoothly. As described above, according to the rotary tool of the second aspect, it is possible to realize the synchro mechanism of the spindle when the clutch mechanism is connected while suppressing the generation of frictional heat when the spindle is idling.

Next, an embodiment of the present invention will be described with reference to FIG. FIG. 1 shows a rotary tool 20 including a clutch mechanism C1 according to this embodiment. In the present embodiment, a screw driver for screw tightening is illustrated as an example of the rotary tool 20. The clutch mechanism C1 of the present embodiment is different from the conventional clutch mechanism C0 in the configuration for causing the spindle 5 to idle (synchronously rotate) when connected. About the same member and structure as the past, the description is abbreviate | omitted using a same sign.
The drive gear 4 is rotatably supported by the main body case 2 via the intermediate shaft 21. The intermediate shaft 21 is pressed into the support hole 2a of the main body case 2 and is fixed to the main body case 2 in a non-rotatable state. This is different from the conventional configuration in which the intermediate shaft 6 is supported by the body case 2 via the bearing 7 in a rotatable state.
The intermediate shaft 21 in the present embodiment has a stepped shape having a large diameter portion 21a and a small diameter portion 21b coaxially. The drive gear 4 is rotatably supported by the large diameter portion 21a. The rear end portion of the large diameter portion 21a is press-fitted into the support hole 2a.
An intermediate sleeve 22 is attached to the small diameter portion 21b. The intermediate sleeve 22 is supported by the small diameter portion 21b so as to be relatively rotatable. The rear end portion of the intermediate sleeve 22 is abutted against a stepped portion 21c between the large diameter portion 21a and the small diameter portion 21b. The stepped portion 21 c of the intermediate shaft 21 slightly protrudes from the front end surface of the drive gear 4. Therefore, a slight gap is generated between the rear end portion of the intermediate sleeve 22 and the front end surface of the drive gear 4. Since the rear end portion of the intermediate sleeve 22 is not in contact with the front surface of the drive gear 4, the urging force of the compression spring 23 does not act on the drive gear 4. Therefore, the rotational power of the drive gear 4 is moved toward the intermediate sleeve 22 and hence the spindle side. Does not work at all.
Further, the front end portion of the intermediate sleeve 22 protrudes slightly forward from the front end of the small diameter portion 21b. The intermediate sleeve 22 and the small diameter portion 21 b of the intermediate shaft 21 enter the support hole 5 c of the spindle 5. The spindle 5 is supported via an intermediate sleeve 22, a small diameter portion 21 b and a bearing 8 so as to be rotatable about an axis and displaceable in the axial direction. The intermediate sleeve 22 is made of a material having a small frictional resistance and a high slidability. Therefore, the intermediate sleeve 22 has a function as a bearing for rotatably supporting the spindle 5 with respect to the small diameter portion 21 b of the intermediate shaft 21.

A compression spring 23 is interposed between the bottom of the support hole 5 c of the spindle 5 and the front end of the intermediate sleeve 22. The compression spring 23 corresponds to the conventional compression spring 10, but is different from the conventional one in that it is in contact with the front end portion of the intermediate sleeve 22 instead of the intermediate shaft 21 in this embodiment. . For this reason, in the state where the spindle 5 rotates with respect to the intermediate shaft 21, the intermediate sleeve 22 rotates relative to the small diameter portion 21b with almost no frictional resistance. Since no relative rotation occurs between the compression spring 23 and the bottom of the support hole 5c, no frictional heat is generated.
By this compression spring 23, the spindle 5 is urged to the front side (the cutoff side of the clutch mechanism C1). Further, the compression sleeve 23 biases the intermediate sleeve 22 in a direction in which the rear end thereof abuts against the stepped portion 21 c of the intermediate shaft 21. A vent hole 5d is provided at the back of the support hole 5c. Through the vent hole 5d, the inner portion of the support hole 5c communicates with the outside to allow ventilation, so that the intermediate sleeve 22 and the small diameter portion 21b of the intermediate shaft 21 are smoother in the axial direction relative to the support hole 5c. As a result, the spindle 5 moves smoothly in the axial direction.
When the spindle 5 is moved backward relative to the compression spring 23 by a pressing operation of the rotary tool 20 toward the screw tightening material (right side in FIG. 1), the clutch mechanism C1 is connected.
The clutch mechanism C <b> 1 includes clutch teeth 4 a to 4 a provided on the front surface of the drive gear 4 and clutch teeth 5 a to 5 a provided on the rear surface of the flange portion 5 b of the spindle 5. The clutch teeth 4a to 4a and the clutch teeth 5a to 5a are engaged with each other by the retraction of the spindle 5, whereby the rotational power of the drive gear 4 is transmitted to the spindle 5. Is made. This is the same as in the prior art.

The clutch mechanism C1 in the present embodiment is a so-called silent clutch. When the screw tightening is completed with the rotary tool 20 pressed, the clutch teeth 4a on the drive gear 4 side are instantaneously detached from the clutch teeth 5a on the spindle 5 side. The clutch mechanism C1 is disconnected, and then the drive gear 4 is idled. This silent clutch is the same as the conventional one, and will be briefly described below.
As described above, the drive gear 4 is supported by the large-diameter portion 21a of the intermediate shaft 21 so as to be rotatable and movable in the axial direction. A thrust bearing 13 is interposed between the rear surface of the drive gear 4 and the mouth end surface (main body case 2) of the support hole 2a. The thrust bearing 13 supports the drive gear 4 so as to be rotatable around the axis of the intermediate shaft 21 while receiving an axial pressing force (axial force) from the spindle 5.
Three engagement pins 12 to 12 are supported on the drive gear 4. The engagement pins 12 to 12 are supported at positions that are equally divided in the circumferential direction around the axis of the intermediate shaft 21 (around the rotation axis of the drive shaft 4). Each engagement pin 12 is supported so as to be tilted by a certain angle from the illustrated upright position (position whose axis is positioned parallel to the rotation axis of the drive gear 4) to the rear side in the rotation direction of the drive gear 4. Yes.
In the upright state, each engagement pin 12 protrudes from the front surface of the drive gear 4 by a certain dimension on the front end side. On the other hand, when each engagement pin 12 tilts rearward in the rotation direction, the rear end corner portion protrudes from the rear surface of the drive gear 4. The rear end surface of each engagement pin 12 is in contact with the front surface of the thrust bearing 13. For this reason, when each engagement pin 12 tilts and the rear end corner portion protrudes from the rear surface of the drive gear 4, the drive gear 4 is displaced in a direction (front side) away from the thrust bearing 13. When the drive gear 4 is displaced forward, the clutch teeth 4a to 4a and the clutch teeth 5a to 5a of the spindle 5 are instantaneously engaged.

When the rotary tool 1 is pressed in the screw tightening direction while the drive gear 4 is idling, the spindle 5 moves backward and the clutch teeth 5a to 5a approach the drive gear 4 side. In the process of retreating the spindle 5, the spindle 4 starts rotating (synchronized rotation) in synchronization with the drive gear 4 by a sync member 25 described later. When the spindle 5 is further retracted while the synchronous rotation is performed and the clutch teeth 5a to 5a approach the drive gear 4, the clutch teeth 5a to 5a come into contact with the front end portions of the three engagement pins 12 to 12. When the clutch teeth 5 a to 5 a come into contact with each other, the three engagement pins 12 to 12 are tilted to the rear side in the rotation direction of the drive gear 4 due to the resistance. When the engaging pins 12 to 12 are tilted, the drive gear 4 moves forward as described above, whereby the clutch teeth 4a to 4a are instantaneously engaged with the clutch teeth 5a to 5a. When the drive gear 4 moves forward due to the inclination of the engagement pins 12 to 12, the intermediate sleeve 22 is pushed forward against the compression spring 23, and at this stage, the urging force of the compression spring 23 is applied to the drive gear 4. It will be in a state of acting temporarily.
The drive gear 4 moves forward against the compression spring 23 and the clutch teeth 4a to 4a are engaged with the clutch teeth 5a to 5a of the spindle 5, whereby the drive gear 4 and the spindle 5 are directly connected for transmission of rotational power. Then, the rotational torque for screw tightening is output to the bit 9, and screw tightening is thereby performed. When the screw tightening proceeds, the front end of the stopper sleeve 14 provided at the front portion of the main body case 2 comes into contact with the screw tightening material, and then the screw tightening proceeds further so that the spindle 5 gradually advances relative to the main body case 2. .
When the screw tightening reaches the set depth in this way, the spindle 5 is returned to the forward end. For this reason, the clutch teeth 5a to 5a are disengaged from the clutch teeth 4a to 4a of the drive gear 4, and the engagement to the engagement pins 12 to 12 is released. As described above, in the engaged state of the clutch mechanism C 1, the urging force of the compression spring 23 acts indirectly via the intermediate sleeve 22 as a result of the drive gear 4 moving forward. For this reason, when the clutch teeth 5 a to 5 a of the spindle 5 are disengaged from the engagement pins 12 to 12, each engagement pin 12 is moved by the urging force of the compression spring 23 that indirectly acts on the drive gear 4 via the intermediate sleeve 22. As a result, the drive gear 4 is returned to the rear side (position where it abuts against the thrust bearing 13). When the drive gear 4 is returned to the rear side in this way, a clearance is instantaneously generated between the clutch teeth 4a to 4a and the clutch teeth 5a to 5a of the spindle 5, so that the drive gear 4 can idle freely. It becomes a cut-off state.

A metal sync member 25 is attached around the flange portion 5 b of the spindle 5. The sync member 25 is attached so as to be wound around the entire circumference of the flange portion 5b. The sync member 25 is provided so as to protrude rearward from the rear surface of the flange portion 5b over the entire circumference. The sync member 25 moves integrally with the spindle 5 in the axial direction (front-rear direction), and rotates around the axis integrally. As shown in FIG. 1, the synchro member 25 is not in contact with the drive gear 4 in a state where the spindle 5 is located at the rotational power cutoff position.
When the spindle 5 is relatively retracted by the pressing operation of the rotary tool 20, first, the sync member 25 comes into contact with the peripheral edge of the drive gear 4. However, when the sync member 25 starts to contact the periphery of the drive gear 4, the clutch teeth 5a to 5a are not yet engaged with the engagement pins 12 to 12 and are not engaged with the clutch teeth 4a to 4a of the drive gear 4. . Therefore, part of the rotational power of the drive gear 4 is transmitted to the spindle 5 by the frictional force of the synchro member 25 immediately before the engagement pins 12 to 12 are engaged with the clutch teeth 5a to 5a. Synchronized rotation (idling) starts in synchronization with 4.
Thus, when the spindle 5 further moves backward while being synchronized, the clutch teeth 5a to 5a engage with the engaging pins 12 to 12 as described above, and each engaging pin 12 tilts rearward in the rotational direction of the drive gear 4. Then, the drive gear 4 moves forward, and the clutch teeth 4a to 4a are instantaneously engaged with the clutch teeth 5a to 5a, and the clutch mechanism C1 is connected. By connecting the clutch mechanism C1 in this way, the rotational power of the drive gear 4 is directly transmitted to the spindle 5. Thus, in addition to the function that the drive gear 4 moves forward due to the inclination of the engagement pins 12 to 12 and the clutch teeth 4a and 5a are instantaneously engaged, the spindle 5 is connected to the drive gear 4 via the sync member 25. Since the clutch teeth 4a to 4a and the clutch teeth 5a to 5a are meshed with each other while being synchronized, the meshing is smoothly performed.

As the screw tightening progresses, the spindle 5 advances, and when the screw tightening is completed, the clutch teeth 5a to 5a of the spindle 5 are disengaged from the clutch teeth 4a to 4a of the drive gear 4 and from the engagement pins 12 to 12. . When the clutch teeth 5a to 5a are disengaged from the engagement pins 12 to 12, the external force for tilting each engagement pin 12 is removed. For this reason, the drive gear 4 moves backward by the urging force of the compression spring 23 that acts indirectly via the intermediate sleeve 22. As a result of the drive gear 4 retreating, the rear end corner of each engagement pin 12 is returned to a position where it does not protrude to the rear surface side, and thus each engagement pin 12 is returned to the upright position. Thus, when the drive gear 4 itself is returned to the rear side, an appropriate clearance is instantly generated between the clutch teeth 4a to 4a and the clutch teeth 5a to 5a of the spindle 5 as shown in the figure. For this reason, the drive gear 4 is idly rotated without generating noise due to mutual interference between the clutch teeth 4a and the clutch teeth 5a or between the clutch teeth 5a and the engagement pins 12. When the pulling operation of the switch lever (not shown) is released, the electric motor 3 is stopped, and thus the drive gear 4 is stopped.
When the user releases the pressing operation of the rotary tool 20, the spindle 5 is returned to the power cutoff position by the urging force of the compression spring 23 as described above. When the spindle 5 is returned to the power cut-off position, the sync member 25 is completely detached from the peripheral edge of the drive gear 4 and the transmission of rotational power between the drive gear 4 and the spindle 5 is completely cut off. For this reason, even if the drive gear 4 is still rotating in this rotational power cut-off state, the intermediate shaft 21 does not rotate. Therefore, the intermediate sleeve 22 and the compression spring are interposed between the intermediate shaft 21 and the intermediate sleeve 22. 23, the compression spring 23 and the spindle 5, and the intermediate sleeve 22 and the spindle 5 do not generate relative rotation, and therefore no frictional heat is generated.
Further, when the spindle 5 is returned to the rotational power cutoff position, the transmission of the rotational power from the drive gear 4 is completely cut off, so that the rotational power for so-called rotation is not transmitted. 11 is omitted. In addition, it is good also as a structure which uses the brake member 11 like the past.

According to the rotary tool 20 of the present embodiment configured as described above, the intermediate shaft 21 that rotatably supports the drive gear 4 is fixed to the main body case 2 in a non-rotatable manner unlike the conventional case. Further, the rear end portion of the intermediate sleeve 22 contacts the stepped portion 21 c of the intermediate shaft 21 and does not contact the front surface of the drive gear 4. For this reason, in the state where the spindle 5 is returned to the rotational power cut-off position, the intermediate shaft 21 and the intermediate sleeve 22, the intermediate sleeve 22 and the compression spring 23, the compression spring 23 and the bottom of the support hole 5c Since no relative rotation occurs between the inner peripheral surface of the support hole 5c and the intermediate sleeve 22, no frictional heat is generated, thereby enhancing the durability of the clutch mechanism C1.
Further, when the user pushes down the rotary tool 20 toward the screw tightening material and the spindle 5 moves backward from the rotational power cutoff position, the synchro member 25 comes into contact with the front peripheral edge of the drive gear 4 and A part of the rotational power of the drive gear 4 is transmitted to the spindle 5 via the sync member 25, whereby the spindle 5 rotates synchronously with the drive gear 4 (synchronous rotation), so that the clutch teeth 5a-5a and the engagement pin 12 And the engagement of the clutch teeth 4a to 4a and the clutch teeth 5a to 5a are smoothly performed. In this way, it is possible to suppress the generation of frictional heat in the rotational power cutoff state without impairing the conventional synchro function.
Further, when the pressing operation of the rotary tool 20 is released and the spindle 5 is returned to the rotational power cut-off position, the rotational power is completely transmitted to the spindle 5 side even when the drive gear 4 is idling. Therefore, even if the conventional brake member 11 is omitted, the joint rotation can be reliably prevented.
Various modifications can be made to the embodiment described above. For example, although the configuration in which the sync member 25 is attached to the spindle 5 is illustrated, a configuration in which the sync member 25 is attached to the drive gear 4 side is also possible.
Moreover, although the meshing type clutch mechanism provided with the clutch teeth 4a to 4a and 5a to 5a has been exemplified, the present invention can be similarly applied to other types of clutch mechanisms such as a friction clutch and an electromagnetic clutch.
Furthermore, the present invention is not limited to the screw tightening machine such as the illustrated screw driver, and can be similarly applied to a clutch mechanism in other forms of rotary tools that output rotational power.

It is a side view which shows the internal structure of the rotary tool provided with the clutch mechanism which concerns on this embodiment. In this figure, the clutch mechanism and its periphery are shown at the front of the rotary tool. It is a side view which shows the internal structure of the rotary tool provided with the conventional clutch mechanism.

Explanation of symbols

1 ... Screw driver (conventional)
2 ... Body case C0 ... Clutch mechanism 3 ... Electric motor 4 ... Drive gear 4a ... Clutch tooth 5 ... Spindle 5a ... Clutch tooth, 5b ... Flange part, 5c ... Support hole, 5d ... Vent hole 6 ... Intermediate shaft 7 ... Bearing 8 ... Bearing 9 ... Bit 10 ... Compression spring 11 ... Brake member 12 ... Engagement pin 13 ... Thrust bearing 14 ... Stopper sleeve 20 ... Rotating tool (this embodiment)
21 ... Intermediate shaft, 21a ... Large diameter part, 21b ... Small diameter part, 21c ... Stepped part C1 ... Clutch mechanism (this embodiment)
22 ... Intermediate sleeve 23 ... Compression spring 25 ... Synchro member

Claims (2)

An electric motor is incorporated in the main body case as a drive source, and includes a drive gear that is rotated by the electric motor, and a spindle that is connected to the drive gear via a clutch mechanism to rotate, and the drive gear is provided in the main body case. The spindle is rotatably supported by the intermediate shaft, and the spindle is supported by the intermediate shaft so as to be rotatable and displaceable in the axial direction. When the spindle moves backward in the axial direction and approaches the drive gear, the clutch A rotary tool that disconnects the clutch mechanism when the mechanism is connected while the spindle advances in the axial direction and moves away from the drive gear;
The intermediate shaft is provided in a state of being non-rotatably fixed to the main body case, and the spindle is rotatably supported by the intermediate shaft via an intermediate sleeve and is interposed between the intermediate sleeve and the intermediate sleeve. A rotary tool configured such that the intermediate sleeve, the compression spring, and the spindle rotate integrally with respect to the intermediate shaft by being biased in a direction away from the drive gear via a compression spring. 2. The rotary tool according to claim 1, wherein a synchro member is provided on at least one of the drive gear or the spindle, and when the spindle moves backward, the rotational power of the drive gear is transmitted to the spindle by friction caused by contact of the synchro member. When the spindle moves forward, the synchro member is separated and the rotational power transmission path between the drive gear and the spindle via the synchro member is cut off.

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