JP2024018365A - Handle and work machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a handle of which an attachment state to a work machine can be finely adjusted, and a work machine comprising the handle of which fine adjustment of the attachment state is possible.

SOLUTION: A sub handle 600 comprises a mount part 601 with an annular shape having a clearance 614 at a part in circumferential direction and engages with a front case 340 of a work machine 1. The mount part 601 has a first detent recess 616 of which a length in a circumferential direction is long, and a second detent recess 617 of which a length in a circumferential direction is short. When the first detent recess 616 of the mount part 601 and a detent protrusion 349 of the front case 340 irregularly engage with each other, since the length of the first detent recess 616 in the circumferential direction is longer than the length of the detent protrusion 349 in the circumferential direction, the sub handle 600 is rotatable with respect to the work machine 1 within a prescribed angle range in a storage state, that is, fine adjustment in an attachment state thereof becomes possible.

SELECTED DRAWING: Figure 39

COPYRIGHT: (C)2024,JPO&INPIT

Description

The present invention relates to a handle and a working machine.

Patent Documents 1 and 2 below disclose working machines such as driver drills. Patent Document 3 below discloses a working machine with a detachable handle.

A work machine such as a driver drill has a motor, a spindle, a transmission mechanism that transmits the rotation of the motor to the spindle, a chuck screwed to the spindle, a reduction ratio switching mechanism that switches the reduction ratio of the transmission mechanism, and a transmission mechanism. and a clutch mechanism that interrupts rotation transmission from the spindle to the spindle at a predetermined torque.

The reduction ratio switching mechanism includes a shift knob that is operated by a user, and a shift arm that moves a slide ring gear of the transmission mechanism forward and backward in conjunction with the operation of the shift knob. The clutch mechanism has a clutch dial for the user to change the predetermined torque. A driver drill having a vibration function as disclosed in Patent Document 2 is also called a vibration driver drill, and the presence or absence of vibration can be switched by operating a clutch dial.

Japanese Patent Application Publication No. 2014-018914 Japanese Patent Application Publication No. 2015-191735 Japanese Patent Application Publication No. 2017-80853

In working machines such as driver drills, the chuck and spindle are fixed with high torque, and a special jig is required to release the fixation. That is, in the absence of a special jig, the chuck and spindle become a substantially integrated tip tool holder. For this reason, it is difficult to replace parts that cannot be removed without releasing the fixation between the chuck and the spindle. Conventional work machines had many parts that were difficult to replace, and repairability was poor. The first problem recognized by the present inventor is to provide a working machine with good repairability.

A working machine such as a driver drill is set in a drill mode where the torque is maximum by fixing the ring gear of the transmission mechanism so that it cannot rotate. As a configuration for setting the drill mode, there is a configuration in which the stopper pin is pushed toward the ring gear by a nut that rotates together with the clutch dial and moves in the axial direction. Here, depending on the rotational position of the ring gear, a part of the ring gear may exist on the extension of the stopper pin. In the above configuration, if the stopper pin hits the part, the clutch dial cannot be rotated and the drill mode cannot be entered, making it inconvenient to use. The second problem recognized by the present inventor is to provide a working machine that can suppress the problem of not being able to make the ring gear non-rotatable.

In a work machine such as a driver drill, if the transmission mechanism is housed in multiple cases separated in the front and back direction, the rigidity of the case can be increased by fixing the multiple cases in the front and back direction with fixing parts such as screws. Deformation can be suppressed. Here, in a configuration in which the shift arm passes outside the fixed portion in the radial direction of the case, the product becomes larger in the radial direction. The third problem recognized by the present inventor is to provide a working machine that can suppress the increase in size.

In a working machine such as a vibrating driver drill, if the amount of clutch dial operation required to switch between the presence and absence of vibration is large, it takes time and effort to switch between the presence and absence of vibration, resulting in poor workability. The fourth problem recognized by the present inventor is to provide a working machine that can reduce the effort required to switch between the presence and absence of vibration.

2. Description of the Related Art As a configuration of a handle that can be attached to and detached from a working machine, a configuration is known in which the handle is attached to a working machine by closing a gap between an annular mount part having a gap (opening) in a part of the circumference. In this configuration, if the maximum length of the gap between the mount portions is the natural length, it may be difficult to attach and detach the handle. A fifth problem recognized by the present inventor is to provide a handle that can be easily attached to and removed from a working machine, and a working machine that includes a handle that is easy to attach and detach.

If the handle cannot be moved while attached to the work machine, it may be inconvenient to make fine adjustments to the attachment state of the handle. A sixth problem recognized by the present inventors is to provide a handle that allows fine adjustment of the attachment state to a work machine, and a work machine equipped with a handle that allows fine adjustment of the attachment state.

An object of the present invention is to provide a handle and a working machine that solve at least the sixth problem among the above problems.

An aspect of the present invention is a handle that is detachable from a working machine,
The mount part is annular and has a plurality of detent parts arranged in the circumferential direction on the inner periphery and engages with the handle attachment part of the working machine,
The plurality of detent portions are
a first detent portion having a long length in the circumferential direction;
and a second detent portion having a short length in the circumferential direction.

Another aspect of the present invention is a working machine with a detachable handle,
a handle attachment part having a rotation regulating part on the outer periphery;
a handle that is annular and has a first rotation stopper on its inner circumference and has a mount portion that engages with the outer circumference of the handle attachment portion of the working machine;
The state of engagement between the first detent portion and the rotation restriction portion is as follows:
a first engaged state in which one end side ends of the first rotation stopper and the rotation restriction part in the circumferential direction are engaged with each other;
It is possible to switch between a second engagement state in which the first rotation stopper and the rotation restriction part are spaced apart from each other in the circumferential direction.

The working machine of the present invention may be expressed as an "electric working machine", "power tool", "electrical equipment", etc., and such expressions are also effective as aspects of the present invention.

According to the present invention, it is possible to provide a handle and a working machine that solve at least the sixth problem among the above problems.

FIG. 1 is a perspective view of a working machine 1 according to an embodiment of the present invention, seen from the front side. FIG. 2 is a perspective view of the working machine 1 seen from the rear side. A right side view of the working machine 1. FIG. 2 is a right side sectional view of the working machine 1. FIG. 3 is an enlarged right sectional view showing the configuration of the transmission/output component 4 of the working machine 1. FIG. FIG. 4 is an exploded perspective view of the transmission/output component 4 as seen from the front side. FIG. 4 is an exploded perspective view of the transmission/output component 4 as seen from the rear side. (A) is a perspective view of the rear case 60 shown in FIGS. 5 to 7, viewed from the front side. (B) is a perspective view of the rear case 60 seen from the rear side. (C) is a front view of the rear case 60. (D) is a sectional view taken along line AA in FIG. 8(C). (E) is a cross-sectional view taken along line BB in FIG. 8(C). (F) is a rear view of the rear case 60. (G) is a right side view of the rear case 60. (A) is a perspective view of the final ring gear 90 that appears in FIGS. 5 to 7, viewed from the front side. (B) is a perspective view of the final ring gear 90 seen from the rear side. (C) is a front view of the final ring gear 90. (D) is a sectional view taken along line AA in FIG. 9(C). (E) is a cross-sectional view taken along line BB in FIG. 9(C). (F) is a rear view of the final ring gear 90. (G) is a right side view of the final ring gear 90. (A) to (D) are perspective views of the stopper block 120 that appears in FIGS. 5 to 7, viewed from different viewpoints. (E) is a front view of the stopper block 120. (F) is a sectional view taken along line AA in FIG. 10(E). (G) is a rear view of the stopper block 120. (G) is a right side view of the stopper block 120. (A) is a perspective view of the gear case 140 that appears in FIGS. 5 to 7. (B) is a front view of the gear case 140. (C) is a sectional view taken along line AA in FIG. 11(B). (D) is a rear view of the gear case 140. (E) is a right side view of the gear case 140. (A) is a perspective view of the rear stopper cam ring 210 shown in FIGS. 5 to 7, viewed from the front side. (B) is a perspective view of the rear stopper cam ring 210 seen from the rear side. (C) is a front view of the rear stopper cam ring 210. (D) is a sectional view taken along line AA in FIG. 12(C). (E) is a cross-sectional view taken along line BB in FIG. 12(C). (F) is a rear view of the rear stopper cam ring 210. (G) is a right side view of the rear stopper cam ring 210. (A) is a perspective view of the front stopper cam ring 230 that appears in FIGS. 5 to 7, viewed from the front side. (B) is a perspective view of the front stopper cam ring 230 seen from the rear side. (C) is a front view of the front stopper cam ring 230. (D) is a sectional view taken along line AA in FIG. 13(C). (E) is a cross-sectional view taken along line BB in FIG. 13(C). (F) is a rear view of the front stopper cam ring 230. (G) is a right side view of the front stopper cam ring 230. (A) is a perspective view of the nut 260 that appears in FIGS. 5 to 7. (B) is a front view of the nut 260. (C) is a sectional view taken along line AA in FIG. 14(B). (D) is a rear view of the nut 260. (E) is a right side view of the nut 260. (A) is a perspective view of the ratchet cam ring 280 shown in FIGS. 5 to 7, viewed from the front side. (B) is a perspective view of the ratchet cam ring 280 seen from the rear side. (C) is a front view of the ratchet cam ring 280. (D) is a sectional view taken along line AA in FIG. 15(C). (E) is a cross-sectional view taken along line BB in FIG. 15(C). (F) is a rear view of the ratchet cam ring 280. (G) is a right side view of the ratchet cam ring 280. (A) is a perspective view of the clutch dial 300 shown in FIGS. 5 to 7, viewed from the front side. (B) is a perspective view of the clutch dial 300 seen from the rear side. (C) is a front view of the clutch dial 300. (D) is a sectional view taken along line AA in FIG. 16(C). (E) is a rear view of the clutch dial 300. (F) is a right side view of the clutch dial 300. (A) is a perspective view of the front case 340 that appears in FIGS. 5 to 7. (B) is a front view of the front case 340. (C) is a sectional view taken along line AA in FIG. 17(B). (D) is a rear view of the front case 340. (E) is a right side view of the front case 340. (A) is a perspective view of the clutch hub 370 that appears in FIGS. 5 to 7. (B) is a front view of the clutch hub 370. (C) is a sectional view taken along line AA in FIG. 18(B). (D) is a rear view of the clutch hub 370. (E) is a right side view of the clutch hub 370. (A) is a perspective view of the rear ratchet 410 shown in FIGS. 5 to 7, viewed from the front side. (B) is a perspective view of the rear ratchet 410 seen from the rear side. (C) is a front view of the rear ratchet 410. (D) is a sectional view taken along line AA in FIG. 19(C). (E) is a rear view of the rear ratchet 410. (F) is a right side view of the rear ratchet 410. (A) is a perspective view of the front ratchet 440 that appears in FIGS. 5 to 7, viewed from the front side. (B) is a perspective view of the front ratchet 440 seen from the rear side. (C) is a front view of the front ratchet 440. (D) is a left side view of the front ratchet 440. (E) is a rear view of the front ratchet 440. (F) is a sectional view taken along line AA in FIG. 20(E). FIG. 3 is a right sectional view of the transmission/output configuration section 4 separated into a transmission section 5, an output switching section 6, and an output section 7; (A) is a front view of the clutch hub 370 and rear ratchet 410. (B) is a sectional view taken along the line AA in FIG. 22(A), showing the positional relationship between the locking protrusion 373 of the clutch hub 370 and the locking protrusion 412 of the rear ratchet 410 in a mode other than the vibration mode. figure. (C) is a sectional view taken along line AA in FIG. 22(A), showing the positional relationship between the locking protrusion 373 of the clutch hub 370 and the locking protrusion 412 of the rear ratchet 410 in the vibration mode. . An explanatory diagram of engagement with. (A) to (E) are diagrams illustrating the configuration of the main parts of the working machine 1 in the clutch mode and the set tightening torque set to the minimum, as seen from different viewpoints, with some parts cut away. (A) to (E) are diagrams illustrating the configuration of the main parts of the work machine 1 in the clutch mode and the set tightening torque set to the maximum, as seen from different viewpoints, with some parts cut away. (A) to (E) are diagrams illustrating the configuration of main parts of the work machine 1 set in the drill mode, viewed from different viewpoints, with some parts cut away. (A) to (E) are diagrams illustrating the configuration of main parts of the work machine 1 set in the vibration mode as seen from different viewpoints, with some parts cut away. FIG. 4 is a perspective view of the transmission/output component 4 seen from the rear. FIG. 4 is a left side view of the transmission/output component 4. FIG. FIG. 4 is a rear view of the transmission/output component 4. FIG. FIG. 4 is a back sectional view of the transmission/output component 4, taken at the engagement portion between the shift arm 71 and the slide ring gear 57; FIG. 3 is a perspective view of the upper part of the working machine 1 with the sub-handle 600 attached thereto, seen from the front. FIG. 3 is a perspective view of the upper part of the work machine 1 with the sub-handle 600 attached, seen from the rear. FIG. 3 is a front view of the work machine 1 with the sub-handle 600 attached. FIG. 3 is a front sectional view of the working machine 1 with the sub-handle 600 attached. FIG. 6 is a front sectional view of the sub-handle 600. FIG. 6 is an exploded perspective view of a sub-handle 600. FIG. 37 is an exploded perspective view of the sub-handle 600 seen from a different perspective from FIG. 36. FIG. 7 is an explanatory diagram of the openable/closable range of the mount portion 601 of the sub-handle 600. FIG. 6 is a diagram showing that the sub-handle 600 is rotatable within a predetermined angle range in the stored state.

This embodiment relates to a working machine 1. The work machine 1 is a vibrating driver drill. 3 and 4 define mutually orthogonal longitudinal and vertical directions of the working machine 1. In addition, the left and right directions perpendicular to the front-rear and up-down directions are defined based on the worker facing forward.

The front-rear direction is a direction parallel to the axial direction of the motor shaft 31. The front side corresponds to one side in the axial direction. The rear side corresponds to the other side in the axial direction. The up-down direction is a direction that connects the motor housing section 11 and the battery pack mounting section 13 perpendicularly to the front-back direction.

As shown in FIGS. 1 to 4, the working machine 1 includes a housing 10. As shown in FIGS. The housing 10 is, for example, a resin molded body having a left-right and left-right split structure. The housing 10 has a motor housing section 11, a handle section 12, and a battery pack mounting section 13.

The motor housing portion 11 is a cylindrical portion whose central axis is parallel to the front-rear direction. The work machine 1 includes a tail cover 15 that covers the rear opening of the motor housing section 11. The work machine 1 includes a shift knob 21 above the motor accommodating portion 11 . The shift knob 21 is a reduction ratio switching operation unit that rotates a shift arm 71 shown in FIGS. 5 to 7 to move a slide ring gear 57 (described later) back and forth, thereby switching the reduction ratio of the transmission mechanism 50 shown in FIG. The shift arm 71 is made of metal, for example, and corresponds to a reduction ratio switching section.

The handle portion 12 extends downward from the lower portion of the motor housing portion 11 . The work machine 1 includes a trigger switch 17 at the upper end of the handle portion 12, which can switch between driving and stopping the motor 30. The working machine 1 is provided with a forward/reverse switch 19 at the boundary between the motor accommodating portion 11 and the handle portion 12, which is capable of switching the motor 30 between forward and reverse rotation.

The battery pack attachment part 13 is connected to the lower end of the handle part 12. The battery pack mounting section 13 removably mounts a battery pack 25 that serves as a power source for the working machine 1. As shown in FIG. 4, the working machine 1 includes a control board section 23 within the battery pack mounting section 13. The control board section 23 is equipped with a microcontroller for controlling the driving of the motor 30, an inverter circuit for supplying current to the motor 30, and the like.

As shown in FIG. 4 , the working machine 1 includes a motor 30 , a fan 35 , and a sensor board 37 in the motor accommodating section 11 . The motor 30 is, for example, an inner rotor type brushless motor, and is driven by electric power from the battery pack 25. The motor 30 has a motor shaft 31 that serves as an output shaft. The fan 35 is provided behind the main body of the motor 30 (the portion of the motor 30 excluding the motor shaft 31), rotates together with the motor shaft 31, and generates cooling air to cool the motor 30 and the like. The sensor board 37 is provided in front of the main body of the motor 30. The sensor board 37 is equipped with a magnetic sensor such as a Hall IC that outputs a signal according to the rotational position of the motor 30.

(Configuration of transmission/output configuration section 4)
5 to 20 relate to the configuration of the transmission/output component 4 (transmission/output unit) of the working machine 1, that is, the configuration of the portion in front of the motor 30.

The transmission/output component 4 includes a motor spacer 40 as a lid of the first case.

As shown in FIGS. 6 and 7, the motor spacer 40 has a bearing holding part 41, a gear part 42, and four screw insertion holes 43.

The bearing holding part 41 is located at the center of the rear part of the motor spacer 40. The bearing holding section 41 holds a ball bearing 33 (bearing) that supports the front part of the motor shaft 31, as shown in FIG. The gear portion 42 is provided on the inner peripheral surface of the motor spacer 40. That is, the motor spacer 40 functions as a first stage ring gear of the transmission mechanism 50.

The four screw insertion holes 43 are through holes through which screws 44 are inserted, respectively. The screw 44 is a fixing part that fixes the motor spacer 40 and the rear case 60 to the gear case 140. The two screws 44 on the upper side correspond to the first fixing part, and the two screws 44 on the lower side correspond to the second fixing part. The screw 44 extends in the front-back direction. The screw collar 45 shown in FIGS. 6 and 7 is made of metal, for example, and is a member through which the two upper screws 44 are passed.

The transmission/output component 4 includes a rear case 60 as a cylindrical first case. The rear case 60 is made of resin, for example.

As shown in FIGS. 8(A) to 8(G), the rear case 60 includes a cylindrical portion 61, two screw boss portions 62 as insertion portions, a guide convex portion 63, a guide hole 64, a spring holding hole 65, and a flange portion. 66, has two through holes 67.

The cylindrical portion 61 is a cylindrical portion coaxial with the motor shaft 31 . The screw boss portions 62 are provided at the lower left and lower right portions of the cylindrical portion 61 so as to protrude outward in the radial direction. The through hole 67 passes through the screw boss portion 62 in the front-back direction. The through hole 67 is a portion through which the two lower screws 44 shown in FIGS. 6 and 7 are passed.

The guide protrusion 63 functions as a rotation guide for the shift arm 71. The guide hole 64 is a long hole (groove-shaped hole) through which the shift arm 71 passes, and serves as a guide for movement of the lower part of the shift arm 71 in the front-rear direction. The spring holding hole 65 is a non-through hole that opens at the front surface of the collar portion 66 and holds the rear end portion of the stopper spring 117 shown in FIGS. 5 to 7. The collar portion 66 extends radially outward from the front end of the cylindrical portion 61 .

The left grease cover 68 and right grease cover 69 that appear in FIGS. 6 and 7 are made of resin, for example, and are attached to the left and right sides of the cylindrical portion 61 so as to cover the left and right guide holes 64, and leak from the guide holes 64, respectively. It functions as a space for storing lubricating oil.

The transmission/output component 4 includes a final ring gear 90. Final ring gear 90 is made of metal, for example.

As shown in FIGS. 9A to 9G, the final ring gear 90 includes six outer circumferential protrusions 91 (protrusions), a cylindrical part 92, a collar part 93, a gear part 94, and six front protrusions 95. , has six front recesses 96.

The cylindrical portion 92 is a cylindrical portion coaxial with the motor shaft 31 . The collar portion 93 extends radially outward from the front end of the cylindrical portion 92 . The six outer circumferential convex portions 91 are arranged at equal angular intervals in the circumferential direction, and each protrudes radially outward from the front portion of the outer circumferential surface of the cylindrical portion 92 . The outer circumferential convex portion 91 is provided across the front portion of the outer circumferential surface of the cylindrical portion 92 and the back surface of the collar portion 93 . The gear portion 94 is provided on the inner peripheral surface of the cylindrical portion 92 .

The front protrusion 95 and the front recess 96 are provided on the front surface of the collar 93. The six front recesses 96 are arranged at equal angular intervals in the circumferential direction. The front convex portion 95 is located between adjacent front concave portions 96 . A rear end portion of a clutch pin 131, which will be described later, is pressed into the front recess 96.

The transmission/output configuration section 4 includes a stopper block 120 as a stopper section. The stopper block 120 is made of metal, for example.

As shown in FIGS. 10(A) to 10(H), the stopper block 120 has a base portion 121, a spring holding portion 122, a locking convex portion 123, and a wide convex portion 124.

The base portion 121 is a planar portion (plate portion) along the inner circumferential surface of the gear case 140 . The spring holding portion 122 is a recess provided on the back surface of the base portion 121, and holds the front end portion of the stopper spring 117 shown in FIGS. 5 to 7. Base portion 121 is located between the inner peripheral surface of gear case 140 and the outer peripheral surface of final ring gear 90.

The locking convex portion 123 is provided on one surface of the base portion 121 that faces the outer circumferential surface of the final ring gear 90 . The locking convex portion 123 is a protrusion that engages with an outer peripheral side convex portion 91 of the final ring gear 90 to make the final ring gear 90 unrotatable when it is in a locking position to be described later.

The wide convex portion 124 continues behind the locking convex portion 123 . The width in the circumferential direction is wider than that of the locking convex portion 123. The wide convex portion 124 is provided to form the spring retaining hole 122.

The transmission/output component 4 includes a gear case 140 as a second case. Gear case 140 is made of metal, for example.

As shown in FIGS. 11(A) to (E), the gear case 140 includes a rear cylindrical portion 141, a front wall portion 142, six through holes 143, three detent portions 144, three through holes 145, and a central It has a through hole 146, four through holes 147, detent portion convex portions 148, 149, a front cylindrical portion 150, four screw holes 151, three stopper insertion grooves 152, and three stopper insertion holes 153.

The rear cylindrical portion 141 is a cylindrical portion coaxial with the motor shaft 31 and constitutes a part of the outer shell of the working machine 1 . The front wall part 142 connects the front part of the rear cylindrical part 141 and the rear part of the front cylindrical part 150 and extends to the inside of the front cylindrical part 150 in the radial direction. The six through holes 143 penetrate the front wall portion 142 in the front-rear direction on the radially outer side of the front tubular portion 150, and each hold a pin sleeve 161 (made of metal, for example) shown in FIGS. 6 to 7.

The three anti-rotation parts 144 are arranged at equal angular intervals in the circumferential direction, and each protrudes forward from the front end of the front cylindrical part 150 by being divided into two parts. The rotation prevention portion 144 sandwiches a rotation prevention convex portion 285 of a ratchet cam ring 280, which will be described later, from both sides in the circumferential direction, thereby making the ratchet cam ring 280 unrotatable.

The three through holes 145 penetrate the front wall portion 142 in the front-rear direction on the radially inner side of the front cylindrical portion 150. The through hole 145 is a portion through which the screw 133 shown in FIGS. 5 to 7 is passed, and corresponds to a mounting portion on the transmission unit housing side. The spring washer 135 shown in FIGS. 6 and 7 is made of metal, for example, and is interposed between the head of the screw 133 and the periphery of the through hole 145 to prevent the screw 133 from loosening. The central through hole 146 is a portion through which the spindle 470 passes. The four through holes 147 are portions through which the screws 27 shown in FIG. 1, ie, the screws 27 for fixing the gear case 140 to the motor accommodating portion 11 from the front, are passed.

The anti-rotation protrusions 148 and 149 are protrusions that engage (fit) with anti-rotation recesses 218 and 219 of a rear stopper cam ring 210, which will be described later, to make the rear stopper cam ring 210 unrotatable. The front cylindrical portion 150 is a cylindrical portion that is coaxial with the motor shaft 31 and has a smaller diameter than the rear cylindrical portion 141 . The four screw holes 151 are portions into which the screws 44 shown in FIGS. 6 and 7 are screwed.

The three stopper insertion grooves 152 are grooves provided on the inner circumferential surface of the rear cylindrical portion 141 at equal angular intervals in the circumferential direction, and each extend in the front-rear direction. The base portion 121 of the stopper block 120 fits into each stopper insertion groove 152. The stopper block 120 is guided by the stopper insertion groove 152 and can move in the front-back direction.

The three stopper insertion holes 153 each penetrate the front wall portion 142 in the front-rear direction and communicate with the stopper insertion groove 152. The stopper block 120 can protrude forward from the front wall portion 142 by passing through each stopper insertion hole 153.

The aforementioned motor spacer 40, rear case 60, and gear case 140 are combined with each other by four screws 44, and constitute a transmission unit housing that accommodates the transmission mechanism 50.

The transmission mechanism 50 is a reduction mechanism made of a planetary gear mechanism here, and includes the gear part 42 of the motor spacer 40, the first planet gear 51, the first carrier 55, the slide ring gear 57, the second planet gear 81, and the second carrier 85. , a final planetary gear 87, a final ring gear 90, and a final carrier 101. These parts constituting the transmission mechanism 50 are made of metal, for example.

The needle bearing 53 shown in FIGS. 6 and 7 is interposed between the inner circumferential surface of the first planetary gear 51 and the rearwardly protruding pin of the first carrier 55.

Slide ring gear 57 has a groove 58 that engages with the end of shift arm 71 . The slide ring gear 57 moves back and forth in response to the back and forth movement of the end of the shift arm 71 as the shift arm 71 rotates.

The slide ring gear 57 meshes with the second planetary gear 81 when located at the front. At this time, the slide ring gear 57 is fixed non-rotatably by a shift dog 75 (made of metal, for example), and the transmission mechanism 50 has a high reduction ratio with three-stage reduction.

The slide ring gear 57 meshes with both the first planetary gear 51 and the second planetary gear 81 when located at the rear. At this time, the transmission mechanism 50 has a two-stage reduction and has a low reduction ratio.

The spline hub 105 shown in FIGS. 5 to 7 is made of metal, for example, and is a component that meshes with the inner peripheral part of the final carrier 101 and the outer peripheral part of the rear end of the spindle 470, and transmits the rotation of the final carrier 101 to the spindle 470. . The final carrier 101 is made of metal, for example.

The roller 103 and lock ring 110 shown in FIGS. 6 and 7 are made of metal, for example, and are components for suppressing rotation transmission from the spindle 470 and chuck 500 side to the final carrier 101 side. When attempting to rotate the chuck 500, the roller 103 is caught between the outer periphery of the spline hub 105 and the inner periphery of the lock ring 110 and is fixed. Each component is positioned in such a way that the roller 103 is not fixed when rotation is transmitted from the final carrier 101 side to the spindle 470 and chuck 500 side.

The hub washer 115 shown in FIGS. 6 and 7 is made of metal, for example, and is interposed between the front surface of the spline hub 105 and the back surface of the front wall 142 of the gear case 140 to avoid contact between the gear case 140 and the spline hub 105. , a part to reduce friction.

The transmission/output component 4 includes a rear stopper cam ring 210 as a first cam.

The rear stopper cam ring 210 is located on the front side of the stopper block 120 , contacts the front end of the stopper block 120 , is biased forward by the stopper spring 117 via the stopper block 120 , and is prevented from rotating relative to the gear case 140 . is regulated.

As shown in FIGS. 12A to 12G, the rear stopper cam ring 210 includes a flat portion 211, an outer inclined portion 212, an outer flat portion 213, an inner inclined portion 214, and an inner flat portion 215. , anti-rotation recesses 218 and 219 are provided.

The flat portion 211 is a flat portion provided on the front surface of the rear stopper cam ring 210 and perpendicular to the front-rear direction. The outer peripheral inclined portion 212 is provided on the radially outer portion of the front surface of the rear stopper cam ring 210. The outer peripheral side inclined part 212 is an inclined surface whose one end is connected to the flat part 211 and which is inclined from the flat part 211 so as to go backward as it goes clockwise in a forward view. The outer peripheral flat part 213 is a flat part that extends in the circumferential direction from the other end of the outer peripheral inclined part 212 and is perpendicular to the front-rear direction. The outer peripheral side inclined part 212 and the outer peripheral side flat part 213 constitute a recess or a hole.

The inner peripheral inclined portion 214 is provided on the radially inner portion of the front surface of the rear stopper cam ring 210. The inner circumferential inclined portion 214 is located at a position separated from the outer circumferential inclined portion 212 by approximately 180° in the circumferential direction. The inner circumferential side inclined part 214 is an inclined surface whose one end is connected to the flat part 211 and which is inclined from the flat part 211 so as to go backward as it goes clockwise in a forward view. The inner peripheral flat part 215 is a flat part that extends in the circumferential direction from the other end of the inner peripheral inclined part 214 and is perpendicular to the front-rear direction. The inner peripheral side inclined part 214 and the inner peripheral side flat part 215 constitute a recess or a hole.

The anti-rotation recesses 218 and 219 engage with the anti-rotation protrusions 148 and 149 of the gear case 140 described above, thereby making the rear stopper cam ring 210 unrotatable with respect to the gear case 140.

The transmission/output component 4 includes a front stopper cam ring 230 as a second cam. The front stopper cam ring 230 is made of resin, for example.

The front stopper cam ring 230 is located in front of the rear stopper cam ring 210 and rotates together with the clutch dial 300.

As shown in FIGS. 13A to 13G, the front stopper cam ring 230 has an outer protrusion 232, an inner protrusion 234, and two locking protrusions 235.

The outer peripheral protrusion 232 protrudes rearward from a radially outer portion of the front stopper cam ring 230. The outer circumferential protrusion 232 is a flat or curved plate-like portion that is substantially perpendicular to the radial direction. The radial position of the outer peripheral protrusion 232 is equal to the radial position of the outer peripheral inclined part 212 and the outer peripheral flat part 213 of the rear stopper cam ring 210.

The inner circumferential protrusion 234 protrudes rearward from the radially inner portion of the front stopper cam ring 230. The inner peripheral protrusion 234 is a flat or curved plate-like portion that is substantially perpendicular to the radial direction. The inner protrusion 234 is spaced apart from the outer protrusion 232 by about 180° in the circumferential direction. The radial position of the inner peripheral protrusion 234 is equal to the radial position of the inner peripheral inclined part 214 and the inner peripheral flat part 215 of the rear stopper cam ring 210.

The two locking protrusions 235 protrude forward from the radially outer portion of the front stopper cam ring 230 at positions spaced approximately 180 degrees apart in the circumferential direction. The locking protrusion 235 is a flat or curved plate-like portion substantially perpendicular to the radial direction. The locking protrusion 235 engages (fits) into a locking recess 302 of a clutch dial 300, which will be described later. As a result, the front stopper cam ring 230 rotates together with the clutch dial 300.

The transmission/output component 4 includes a nut 260 as a screw member. The nut 260 is made of resin, for example.

As shown in FIGS. 14(A) to 14(E), the nut 260 has a threaded portion 261, six spring locking holes 262, and three notches 263.

The threaded portion 261 is provided on the outer peripheral surface of the nut 260, and is screwed into a threaded portion 301 of a clutch dial 300, which will be described later. The six spring locking holes 262 are non-through holes arranged at equal angular intervals in the circumferential direction, and each holds the front end portion of the clutch spring 250 (made of metal, for example) shown in FIGS. 5 to 7. The three cutouts 263 are arranged at equal angular intervals in the circumferential direction, and allow the screws 133 shown in FIGS. 5 to 7 to pass through each of the cutouts 263.

The thrust plate 165 shown in FIGS. 6 and 7 is made of metal, for example, and is biased rearward with respect to the nut 260 by the clutch spring 250, pushing the front end of the clutch pin 131 rearward and pushing the front end of the clutch pin 131 backward. Press the end against the front surface of final ring gear 90. The clutch pin 131 is made of metal, for example, and extends in the front-rear direction through a pin sleeve 161 held in the through hole 143 of the gear case 140 described above.

The transmission/output component 4 includes a ratchet cam ring 280 as a cam ring. Ratchet cam ring 280 is made of metal, for example.

As shown in FIGS. 15A to 15G, the ratchet cam ring 280 has an outer protrusion 282, an inner protrusion 284, three anti-rotation protrusions 285, and three small protrusions 288.

The outer peripheral protrusion 282 protrudes forward from a radially outer portion of the ratchet cam ring 280. The outer peripheral protrusion 282 is a flat or curved plate-like portion that is substantially perpendicular to the radial direction.

The inner peripheral protrusion 284 protrudes forward from the radially inner portion of the ratchet cam ring 280. The inner circumferential protrusion 284 is a flat or curved plate-like portion that is substantially perpendicular to the radial direction.

The three anti-rotation protrusions 285 are arranged at equal angular intervals in the circumferential direction, and each protrudes toward the center of the ratchet cam ring 280. The anti-rotation convex portion 285 is sandwiched between the two pronged anti-rotation portions 144 of the gear case 140 described above. This makes the ratchet cam ring 280 unable to rotate relative to the gear case 140. The back surface of the anti-rotation projection 285 contacts the front surface of an outer protrusion 372 of a clutch hub 370, which will be described later, and is pressed forward.

The three small protrusions 288 each protrude radially inward at a position spaced apart from the detent convex portion 285 by a predetermined angle in the circumferential direction. The small protrusion 288 contacts the outer circumferential surface of a threaded boss portion 345 of the front case 340, which will be described later, at a point where the circumferential position of the anti-rotation convex portion 285 and the circumferential position of the outer protrusion portion 372 of the clutch hub 370 coincide with each other. It has the role of positioning.

When setting the ratchet cam ring 280 in front of the clutch hub 370, the outer protrusion 372 of the clutch hub 370 is passed through the circumferential gap between the anti-rotation protrusion 285 and the small protrusion 288. Thereafter, the ratchet cam ring 280 is rotated until the small protrusion 288 contacts the outer circumferential surface of the screw boss portion 345 of the front case 340, and the ratchet cam ring 280 is rotated until the small protrusion 288 contacts the outer peripheral surface of the screw boss portion 345 of the front case 340, and the back surface of the detent convex portion 285 and the front surface of the outer protrusion portion 372 of the clutch hub 370 are ratcheted. The contact is made by the biasing force of the spring 360.

The transmission/output configuration section 4 includes a clutch dial 300 as a switching operation section. The clutch dial 300 is made of resin, for example.

As shown in FIGS. 16A to 16F, the clutch dial 300 includes a threaded portion 301, two locking recesses 302, an inner recess 304, an outer hole 305, a cylindrical portion 306, and a front wall. 307, it has a leaf spring attachment part 308.

The cylindrical portion 306 has a central axis coaxial with the motor shaft 31 and a cross section perpendicular to the front-rear direction that is approximately circular, and the diameter becomes smaller toward the front. The front wall portion 307 extends radially inward from the front end of the cylindrical portion 306 .

The threaded portion 301 is provided on the inner peripheral surface of the cylindrical portion 306. The threaded portion 301 is threadedly engaged with the threaded portion 261 of the nut 260 described above. The clutch dial 300 is sandwiched between the gear case 140 and a front case 340, which will be described later, in the front-rear direction, and its position in the front-rear direction is fixed. Therefore, the nut 260 moves in the front-rear direction in conjunction with the rotation of the clutch dial 300.

The two locking recesses 302 are located approximately 180° apart from each other in the circumferential direction, and are each formed as a notch that is partially cut out from the lower end of the threaded portion 301. The locking recess 302 engages with the locking protrusion 235 of the front stopper cam ring 230 described above, causing the front stopper cam ring 230 to rotate together with the clutch dial 300.

The inner circumferential recess 304 is located at the radially inner portion of the back surface of the front wall 307 . The radial position of the inner circumferential recess 304 is equal to the radial position of the inner circumferential protrusion 284 of the ratchet cam ring 280 described above (or includes the radial position range of the inner circumferential protrusion 284).

The outer circumferential hole portion 305 penetrates the radially outer portion of the front wall portion 307 in the front-rear direction. The radial position of the outer circumferential hole 305 is equal to the radial position of the outer circumferential protrusion 282 of the ratchet cam ring 280 described above (or includes the radial position range of the outer circumferential protrusion 282).

The leaf spring attachment part 308 is a part to which a leaf spring 331 (made of metal, for example) shown in FIGS. 6 and 7 is attached.

The transmission/output component 4 includes a front case 340 as an output housing. Front case 340 is made of metal, for example.

As shown in FIGS. 17(A) to (E), the front case 340 includes a large diameter cylindrical portion 341, a small diameter cylindrical portion 342, a connecting surface portion 343, three notches 344, three screw boss portions 345, and three screws. It has a hole 346, three screw holes 347, a bearing holding part 348, two anti-rotation protrusions 349, two anti-slip protrusions 350, and a locking recess 351.

The large diameter cylindrical portion 341 is a cylindrical portion coaxial with the motor shaft 31 . The small diameter cylindrical portion 342 is a cylindrical portion coaxial with the motor shaft 31 . The small diameter cylindrical portion 342 has a smaller diameter than the large diameter cylindrical portion 341 and is located at the rear of the large diameter cylindrical portion 341 . A ratchet spring 360, a rear ratchet 410, a front ratchet 440, a ball bearing 461, etc. are arranged within the small diameter cylindrical portion 342. The connecting surface portion 343 is a wall portion perpendicular to the front-back direction that connects the rear end portion of the large diameter cylindrical portion 341 and the front end portion of the small diameter cylindrical portion 342.

The three notches 344 are arranged at equal angular intervals in the circumferential direction, and each allows an outer protrusion 372 of a clutch hub 370, which will be described later, to pass therethrough. The three screw boss portions 345 are arranged at equal angular intervals in the circumferential direction, and are provided so as to protrude radially outward from the outer circumferential surface of the small diameter cylindrical portion 342, respectively. The three screw holes 347 are non-through holes that open on the back surface of the screw boss portion 345, and the screws 133 shown in FIGS. 5 to 7 are screwed into each of the three screw holes 347. The screw boss portion 345 and the screw hole 347 correspond to a mounting portion on the output housing side.

The three screw holes 346 are non-through holes that open on the front surface of the connection surface portion 343, and are screwed with the screws 489 shown in FIGS. 5 to 7, respectively. The three screw holes 346 are provided at the same positions as the three screw holes 347 in the circumferential direction. The bearing holding portion 348 holds the ball bearing 335 (bearing) shown in FIGS. 5 to 7. The ball bearing 335 is made of metal, for example, and rotatably supports the rear part of the spindle 470.

The two anti-rotation convex portions 349 are located approximately 180° apart from each other in the circumferential direction, and protrude radially outward from the left and right portions of the outer circumferential surface of the large diameter cylindrical portion 341, respectively. The anti-rotation protrusion 349 engages (fits) with a first anti-rotation recess 616 or a second anti-rotation recess 617 of the sub-handle 600, which will be described later, to prevent rotation of the sub-handle 600 relative to the front case 340. This is the regulatory department.

The two retaining convex portions 350 are located approximately 180° apart from each other in the circumferential direction, and protrude radially outward from the left and right portions of the outer circumferential surface of the large diameter cylindrical portion 341, respectively. The protruding length of the retaining convex portion 350 is shorter than the protruding length of the detent convex portion 349. The retaining convex portion 350 continues from the detent convex portion 349 on both sides in the circumferential direction. The retaining convex portion 350 prevents a sub-handle 600, which will be described later, from slipping forward (separating) from the front case 340.

The locking recess 351 is a groove into which the leaf spring 331 is fitted, and has three types: one corresponding to each step of the set tightening torque in the clutch mode, one corresponding to the drill mode, and one corresponding to the vibration mode. be. By fitting the leaf spring 331 into the locking recess 351, the rotational position of the clutch dial 300 is determined, and the clutch dial 300 is locked in the rotational direction and held so as not to rotate accidentally.

The transmission/output component 4 includes a clutch hub 370.

Clutch hub 370 is a regulating portion that regulates the movement (rotation) of rear ratchet 410 in vibration mode. Clutch hub 370 is made of metal, for example.

As shown in FIGS. 18(A) to 18(E), the clutch hub 370 has an annular portion 371, three outer protrusions 372, and six locking protrusions 373.

The annular portion 371 is a ring portion coaxial with the motor shaft 31 . The three outer protrusions 372 are arranged at equal angular intervals in the circumferential direction, and each protrudes radially outward from the outer circumferential surface of the annular portion 371. The six locking convex portions 373 are protrusions that are arranged at equal angular intervals in the circumferential direction, and each protrude radially inward from the rear portion of the inner circumferential surface of the annular portion 371.

The transmission/output configuration section 4 includes a rear ratchet 410 as a second vibration section. The rear ratchet 410 is made of metal, for example.

As shown in FIGS. 19(A) to 19(F), the rear ratchet 410 is ring-shaped and has an uneven part 411 on the front surface and six locking protrusions 412 on the front part of the outer peripheral surface. . The six locking protrusions 412 are protrusions that are arranged at equal angular intervals in the circumferential direction and each protrudes outward in the radial direction.

The thrust bearing 391 and bearing washer 395 that appear in FIGS. 6 and 7 are made of metal, for example, and are interposed between the back surface of the rear ratchet 410 and the surface of the front case 340 facing thereto, and receive loads in the front-rear direction. . The thrust bearing 391 and the bearing washer 395 reduce friction when the tip tool 20 is pressed against a mating material and suppress power loss.

The transmission/output configuration section 4 includes a front ratchet 440 as a first vibration section. The front ratchet 440 is made of metal, for example.

As shown in FIGS. 20(A) to 20(F), the front ratchet 440 is ring-shaped and has an uneven portion 441 on the back surface. The uneven portion 441 is a vibration-generating shaped portion, and outputs vibration to the spindle 470 by contacting the uneven portion 411 (vibration-generating shaped portion) of the rear ratchet 410 and rotating relative thereto.

The spring 431 shown in FIGS. 5 to 7 is made of metal, for example, and urges the front ratchet 440 forward with respect to the rear ratchet 410. As a result, when the tip tool 20 is not pressed against the mating material, the rear ratchet 410 and the front ratchet 440 are out of contact, and the generation of vibration is suppressed. The ratchet washer 435 is made of metal, for example, and reduces friction by avoiding contact between the front ratchet 440 and the spring 431.

The ball bearing 461 shown in FIGS. 5 to 7 is made of metal, for example, and rotatably supports the front ratchet 440 and the intermediate portion of the spindle 470 with respect to the front case 340. Front ratchet 440 rotates together with spindle 470.

The transmission/output component 4 includes a spindle 470 and a chuck 500. Both the spindle 470 and the chuck 500 are made of metal, for example. The spindle 470 is rotationally driven by the motor 30 via the transmission mechanism 50. The chuck 500 holds the tip tool 20 shown in FIG. 3 and rotates together with the spindle 470.

The chuck 500 is fixed to the spindle 470 by screwing the threaded portion on the rear inner circumferential surface of the chuck 500 to the threaded portion on the front outer circumferential surface of the spindle 470 . Further, the chuck 500 is fixed to the spindle 470 by a left-hand thread 495 (made of metal, for example). The spindle 470 and chuck 500 are rigidly fixed to each other and constitute a substantially integral tool holder.

The bearing cover 485 shown in FIGS. 5 to 7 is made of metal, for example, and is fixed to the front case 340 by screws 489 that pass through its own through hole 487 and are screwed into the screw holes 346 of the front case 340. Ru.

The O-ring 481 shown in FIGS. 5 to 7 is an elastic body such as rubber, and is provided between the inner peripheral surface of the bearing cover 485 and the outer peripheral surface of the spindle 470. The O-ring 481 slides on the inner circumferential surface of the bearing cover 485 and reduces the impact when the rotating hand stops (during braking). The O-ring 481 also has the function of preventing oil leakage.

The retaining ring 483 shown in FIGS. 5 to 7 is made of metal, for example, and is provided on the inner peripheral surface of the small diameter cylindrical portion 342 of the front case 340, and functions to prevent the ball bearing 461 from coming off.

(Disassembly of transmission/output component 4)
FIG. 21 is a right sectional view of the transmission/output component 4 separated into a transmission section 5, an output switching section 6, and an output section 7.

The transmission unit 5 is located in front of the motor 30 and transmits the driving force of the motor 30 to the spindle 470. The transmission section 5 includes a transmission section housing (motor spacer 40, rear case 60, gear case 140) and components held or supported by the transmission section housing (transmission mechanism 50, etc.).

The output switching unit 6 switches the output of the output unit 7, that is, the torque and the presence or absence of vibration. The output switching section 6 is arranged to be sandwiched between the output section 7 and the transmission section 5 in the front-rear direction. The output switching unit 6 includes a clutch dial 300 and various parts (such as the nut 260) held or supported by the clutch dial 300.

The output section 7 includes a front case 340 and components held or supported by the front case 340, such as a spindle 470, a chuck 500, ball bearings 335 and 461, and the like.

The transmission section 5 is detachably attached to the output section 7 from the rear side. Specifically, gear case 140 is assembled to front case 340 from the rear side using screws 133 that pass through through holes 145 of gear case 140 and are screwed into screw holes 347 of front case 340.

The screw 133 is an example of a fixing part that fixes the output part 7 and the transmission part 5. The existing ranges of the screw 133 and the output switching section 6 at least partially overlap. When the fixation by the screws 133 is released, the transmission section 5 can be removed from the output section 7.

When the transmission section 5 is removed from the output section 7, that is, when the screw 133 is removed and the gear case 140 is removed from the front case 340, the output switching section 6 is moved backward from the output section 7 while the spindle 470 and chuck 500 remain fixed. It can be removed from the side.

(clutch mode, drill mode, vibration mode)
The work machine 1 has a clutch mode, a drill mode, and a vibration mode, and any one of the modes can be selected by operating the clutch dial 300.

The clutch mode is a mode in which rotation transmission from the transmission mechanism 50 to the spindle 470 is interrupted when a set tightening torque (predetermined torque) is exceeded, that is, a mode in which the clutch mechanism is effective. The set tightening torque can be adjusted in multiple stages, for example, 22 stages, by operating the clutch dial 300.

23(A) to (E) show a state in which the clutch mode and the set tightening torque are set to the minimum. FIGS. 24(A) to 24(E) show states in which the clutch mode and the set tightening torque are set to the maximum.

The clutch mechanism stops the rotation of the final ring gear 90 until the set tightening torque is reached, but allows the final ring gear 90 to rotate when the set tightening torque is exceeded. The clutch mechanism includes a nut 260, a clutch spring 250, a thrust plate 165, and a clutch pin 131.

When a load (torque) is applied to the tip tool 20 while the motor 30 is driving, the final ring gear 90, which is not fixed, tends to rotate. The clutch pin 131 is located in the front recess 96 of the final ring gear 90 until the set tightening torque is reached. As a result, final ring gear 90 becomes unrotatable, and torque transmission by transmission mechanism 50 becomes effective.

On the other hand, when the torque applied to the tip tool 20 increases and exceeds the set tightening torque, that is, the load (torque) exceeds the force that causes the clutch pin 131 to push the final ring gear 90 backward and stop the rotation of the final ring gear 90. When applied to the final ring gear 90, the final ring gear 90 rotates, and the clutch pin 131 rides over the front protrusion 95 of the final ring gear 90. This is a clutch operation, and torque transmission by the transmission mechanism 50 is interrupted by the clutch mechanism.

The load (set tightening torque) when the clutch mechanism operates is proportional to the amount of compression of the clutch spring 250. When the clutch dial 300 is turned, the nut 260 moves back and forth, and the amount of compression of the clutch spring 250 can be changed.

In the states shown in FIGS. 23A to 23E, the nut 260 is in the most advanced position, and the amount of compression of the clutch spring 250 is the minimum (the set tightening torque is the minimum). When the nut 260 is rotated clockwise when viewed from the front from this state, the nut 260 moves backward, and the amount of compression of the clutch spring 250 increases. In the states shown in FIGS. 24(A) to 24(E), the nut 260 is at the most retracted position, and the amount of compression of the clutch spring 250 is the maximum (the set tightening torque is the highest).

(Switching configuration to drill mode)
The drill mode is a mode in which the final ring gear 90 is made unrotatable regardless of the clutch mechanism, and is a mode in which the working machine 1 can produce the maximum tightening torque.

From the state shown in FIGS. 24(A) to 24(E), that is, the state in which the clutch mode and the set tightening torque are set to the maximum, the clutch dial 300 is further rotated clockwise when viewed from the front to correspond to the drill mode. When set to the position, the state shown in FIGS. 25(A) to 25(E), that is, the drill mode is entered.

The configuration for switching to the drill mode includes a stopper block 120, a stopper spring 117 as a biasing means, a rear stopper cam ring 210, and a front stopper cam ring 230.

Stopper block 120 is movable between a locked position (forward position) and a non-locked position (retracted position), and makes final ring gear 90 unrotatable when in the locked position. The front end of the stopper block 120 projects further forward than the final ring gear 90. The stopper spring 117 is made of metal, for example, and urges the stopper block 120 forward, that is, toward the locking position.

Clutch dial 300 is a switching operation section that can switch the position of stopper block 120 between a locking position and a non-locking position. Clutch dial 300 is located on the front side of final ring gear 90. The clutch dial 300 is rotatable around an extension of the axis of the motor shaft 31.

The rear stopper cam ring 210 and the front stopper cam ring 230 are regulating parts that restrict movement of the stopper block 120 from the non-locking position to the locking position against the bias of the stopper spring 117. By operating the clutch dial 300, regulation and release by the rear stopper cam ring 210 and the front stopper cam ring 230 are switched. That is, the rear stopper cam ring 210 and the front stopper cam ring 230 constitute a cam mechanism that moves the stopper block 120 between the non-locking position and the locking position in conjunction with the rotation of the clutch dial 300.

The rear stopper cam ring 210 is located on the front side of the stopper block 120, and its back surface contacts the stopper block 120. The rear stopper cam ring 210 contacts the stopper block 120 on the outside of the final ring gear 90 in the radial direction of the final ring gear 90. The rear stopper cam ring 210 is located further forward than the final ring gear 90. The rear stopper cam ring 210 is urged forward by the stopper spring 117 via the stopper block 120. The rotation of the rear stopper cam ring 210 with respect to the gear case 140 is restricted by the engagement (fitting) between the rotation prevention protrusions 148 and 149 of the gear case 140 and the rotation prevention recesses 218 and 219 of the rear stopper cam ring 210. .

The front stopper cam ring 230 is located in front of the rear stopper cam ring 210. Due to the engagement (fitting) between the locking protrusion 235 of the front stopper cam ring 230 and the locking recess 302 of the clutch dial 300, the front stopper cam ring 230 rotates together with the clutch dial 300. When the clutch dial 300 reaches a rotation position corresponding to the drill mode, that is, when the front stopper cam ring 230 reaches a predetermined rotation position, the rear stopper cam ring 210 moves forward. This releases the restriction on movement of the stopper block 120 from the non-locking position to the locking position.

The rear stopper cam ring 210 has an outer sloped part 212 and an outer flat part 213 as recesses, and an inner slope 214 and an inner flat part 215 as recesses. The front stopper cam ring 230 has an outer protrusion 232 and an inner protrusion 234 as convex parts. In the process of the front stopper cam ring 230 coming to the predetermined rotational position (the process of the clutch dial 300 coming to the drill mode rotational position), the outer circumferential protrusion 232 and the inner circumferential protrusion 234 are connected to the outer circumferential inclined part 212 and the inner circumferential inclined part. 214, and the rear stopper cam ring 210 moves forward. The slopes of the outer peripheral side inclined part 212 and the inner peripheral side inclined part 214 are preferably steeper than the slope of the threaded part 301 of the clutch dial 300.

24(A) to (E) and FIG. 25(A) to (E), in the process of switching from the clutch mode to the drill mode, the outer circumferential protrusion 232 of the front stopper cam ring 230 is attached to the outer circumference of the rear stopper cam ring 210. Going down the side slope 212, the rear stopper cam ring 210 moves forward due to the bias of the stopper spring 117, and the stopper block 120 appears to move to the locking position (forward position). In the drill mode, the locking convex portion 123 of the stopper block 120 in the locking position engages (abuts in the rotational direction) with the outer peripheral side convex portion 91 of the final ring gear 90, making the final ring gear 90 unrotatable. Note that the locking convex portion 123 of the stopper block 120 in the non-locking position does not engage with the outer peripheral side convex portion 91 of the final ring gear 90, allowing the final ring gear 90 to rotate.

When the clutch dial 300 is within the predetermined rotation range corresponding to the clutch mode described above (rotation position between the states of FIGS. 23(A) to (E) and the states of FIGS. 24(A) to (E)), , the outer protrusion 232 and the inner protrusion 234 of the front stopper cam ring 230 are in contact with the flat part 211 of the rear stopper cam ring 210, and the rear stopper cam ring 210 does not move forward and the stopper block 120 is engaged. It does not move to the stop position.

(Switching configuration to vibration mode)
The vibration mode is a mode in which vibrations in the longitudinal direction are applied to the spindle 470 in the drill mode.

When the clutch dial 300 is further rotated clockwise as seen from the front from the state shown in FIGS. 25(A) to 25(E), that is, the drill mode, to the rotation position corresponding to the vibration mode, the state shown in FIGS. 26(A) to 26(E) is shown. In other words, it becomes a vibration mode.

The configuration for switching to drill mode includes a ratchet cam ring 280, a ratchet spring 360, a clutch hub 370, a rear ratchet 410, and a front ratchet 440.

The rear ratchet 410 and the front ratchet 440 are vibrating parts that output the driving force of the motor 30 as vibration to the spindle 470. The front ratchet 440 is driven (rotated) by the driving force of the motor 30. The clutch dial 300 switches the rear ratchet 410 and the front ratchet 440 between a vibration-on state and a vibration-off state.

The ratchet cam ring 280 and the clutch hub 370 are vibration switching parts that move from a vibration off position (backward position) to a vibration on position (forward position) in accordance with the operation of the clutch dial 300. The ratchet spring 360 is made of metal, for example, and is a biasing portion that biases the ratchet cam ring 280 and the clutch hub 370 forward, that is, toward the vibration-on position.

The outer protrusion 282 and inner protrusion 284 of the ratchet cam ring 280 that appear in FIGS. 15(A) to (E), and (G), and the clutch that appears in FIGS. 16(A) to (C), and (E) The inner recess 304 and outer hole 305 of the dial 300 allow the ratchet cam ring 280 and clutch hub 370 to move from the vibration off position to the vibration on position when the clutch dial 300 comes to a rotational position corresponding to the vibration mode. This is the guide section that guides you through the process.

When the clutch dial 300 reaches the rotational position corresponding to the vibration mode, the outer protrusion 282 of the ratchet cam ring 280 and the outer hole 305 of the clutch dial 300 face each other, and the inner protrusion 284 of the ratchet cam ring 280 faces each other. and the inner circumferential recess 304 of the clutch dial 300 are opposed to each other. Then, the outer protrusion 282 and the inner protrusion 284 of the ratchet cam ring 280 are inserted into the outer hole 305 and the inner recess 304 of the clutch dial 300, respectively, so that the ratchet cam ring 280 is biased by the ratchet spring 360. Cam ring 280 and clutch hub 370 move from the vibration off position to the vibration on position.

The inclined parts 286 and 287 that appear in FIG. 15(G) provided at one circumferential end of the outer protrusion 282 and the inner protrusion 284 of the ratchet cam ring 280 are the outer protrusion 282 and the inner protrusion, respectively. It functions to smoothly move the portion 284 into and out of the outer hole 305 and the inner recess 304 of the clutch dial 300.

The clutch hub 370 does not restrict the movement of the rear ratchet 410 in the vibration off position, and restricts the movement of the rear ratchet 410 in the vibration on position. Vibrations are generated when the front ratchet 440 is driven by the driving force of the motor 30 relative to the rear ratchet 410 whose movement is restricted.

Clutch hub 370 is urged forward by ratchet spring 360 and presses ratchet cam ring 280 forward. The locking convex portion 373 of the clutch hub 370 that appears in FIGS. 18(A) to (D) and the locking convex portion of the rear ratchet 410 that appears in FIGS. 19(A) to (C), (E) to (F) 412 engage with each other as shown in FIGS. 22(C) and 26(D) when the clutch hub 370 is in the vibration-on position.

As shown in FIGS. 22(B) and 22(C), both circumferential sides of the locking protrusion 373 of the clutch hub 370 and the locking protrusion 412 of the rear ratchet 410 cause the clutch hub 370 to vibrate from the vibration-on position. Slanted portions 374, 413 are provided to make it difficult to move to the off position. Using the angle θ shown in FIGS. 22(B) and 22(C), the inclination angle is expressed as θ/2 with respect to the front-rear direction. When the clutch hub 370 is in the vibration-on position, the locking convex portions 373 and 412 have the inclined portions 374 and 413 in contact with each other. When a rotational force is applied to the rear ratchet 410 in this state, a forward force is applied to the clutch hub 370 due to engagement between the inclined parts 374 and 413, making it difficult to move to the vibration off position.

25(A) to (E) and FIG. 26(A) to (E), in the process of switching from the drill mode to the vibration mode, the ratchet cam ring 280 and the clutch hub 370 move forward due to the urging of the ratchet spring 360, It appears that the locking protrusion 373 of the clutch hub 370 and the locking protrusion 412 of the rear ratchet 410 are aligned in the longitudinal direction. In this process, the outer peripheral protrusion 232 and the inner peripheral protrusion 234 of the front stopper cam ring 230 move on the outer peripheral flat part 213 and the inner peripheral flat part 215 of the rear stopper cam ring 210, and the stopper block 120 The rotation regulation of final ring gear 90 is effectively maintained.

When the clutch dial 300 is within the predetermined rotation range corresponding to the clutch mode and drill mode described above (rotational position between the states of FIGS. 23(A) to (E) and the states of FIGS. 25(A) to (E)). At some point, the outer protrusion 282 and the inner protrusion 284 of the ratchet cam ring 280 are in contact with the flat part (the flat part perpendicular to the front-rear direction) of the clutch dial 300, and the ratchet cam ring 280 and the clutch hub 370 will not move forward (will not move to the vibration on position).

(How to pass the shift arm 71)
As described above, the motor spacer 40, the rear case 60, and the gear case 140 are fixed with four screws 44 and constitute a transmission housing. According to this, the rigidity of the transmission part housing as a whole is increased, and deformation when the clutch mechanism is operated, for example, can be suppressed.

On the other hand, in the configuration in which the shift arm 71 is extended in the radial direction of the rear case 60 through the outside of the screw 44 to the guide hole 64 of the rear case 60, the motor accommodating portion 11 that covers the outside of the shift arm 71 becomes larger, leading to an increase in the size of the product. .

As shown in FIGS. 27 to 30, in the working machine 1, the shift arm 71 is extended to the guide hole 64 of the rear case 60 through the inside of the screw 44 in the radial direction of the rear case 60.

When the motor spacer 40, rear case 60, and gear case 140 are fixed by the two upper screws 44, there is a gap between the outer surface of the rear case 60 and the two upper screws 44, and the shift arm 71 is inserted into the gap. extends.

A portion of the two upper screws 44 extending in the front-rear direction on the outside of the rear case 60 is inserted into a screw collar 45 that is a cylindrical portion separate from the rear case 60 . That is, the two upper screws 44 each pass through the screw insertion hole 43 and the screw collar 45 of the motor spacer 40 and are screwed into the screw hole 151 of the gear case 140. The screw collar 45 is used to prevent the motor spacer 40 from being bent or damaged due to over-tightening of the upper two screws 44. The shift arm 71 passes through a gap between the outer circumferential surface of the screw collar 45 and the outer circumferential surface of the rear case 60.

The lower two screws 44 pass through the screw insertion holes 43 of the motor spacer 40 and the through holes 67 of the rear case 60, respectively, and are screwed into the screw holes 151 of the gear case 140. The screw boss portion 62 having the through hole 67 is a part of the rear case 60 (integrated with the rear case 60), and although there is no gap between the screw boss portion 62 and the outer surface of the rear case 60, the shift arm 71 passes through it. Since it is not a part, there is no problem with increasing the size.

(Sub handle 600)
31 to 39 relate to the sub-handle 600 according to this embodiment. 31 to 34 and 39 show the working machine 1 with the sub-handle 600 attached. 35-38 show a single sub-handle 600. FIG. The front case 340 is a handle attachment portion of the working machine 1. Note that the sub-handle 600 is not limited to the mounting configuration in which it extends leftward from the working machine 1 as shown in FIG.

(Opening/closing structure of mount part 601)
The sub-handle 600 includes a mount section 601, a first shaft section 602, and a second shaft section 603.

The mount portion 601 has an annular shape with a gap 614 in a portion in the circumferential direction, and engages with the front case 340 of the working machine 1 . The mount portion 601 has a pin layer through hole 606, a first cylindrical portion 612, a second cylindrical portion 613, and an annular portion 615.

The first cylindrical portion 612 is provided on one side (the left side in FIG. 35) of the gap 614 in the upper part of the annular portion 615 and in the length direction of the gap 614 (hereinafter referred to as the “gap length direction”), and is provided in the gap length direction. Extends to.

The first cylindrical portion 612 has a head holding portion 624 and a shaft insertion portion 626. The head holding section 624 holds the head 610 of the first shaft section 602. The head holding part 624 is located on one side (the left side in FIG. 35) of the shaft insertion part 626 in the gap length direction, and is larger and non-circular than the shaft insertion part 626 when viewed from the gap length direction. For example, the head 610 is fitted in a hexagonal shape. The shaft portion insertion portion 626 is smaller than the head portion 610 when viewed from the length direction of the gap, and the shaft portion 611 of the first shaft portion 602 passes therethrough.

The second cylindrical portion 613 is provided above the annular portion 615 and on one side (the right side in FIG. 35) of the gap 614 in the gap length direction, and extends in the gap length direction. The central axes of the first cylindrical portion 612 and the second cylindrical portion 613 are parallel to the length direction of the gap.

The second cylindrical portion 613 has a shaft insertion portion 627 and an enlarged diameter portion 628. The shaft portion 611 of the first shaft portion 602 passes through the shaft portion insertion portion 627 . The enlarged diameter portion 628 is located on the other side (the right side in FIG. 35) of the shaft insertion portion 627 in the length direction of the gap, has a larger diameter than the shaft insertion portion 627, and has a larger diameter than the shaft insertion portion 627. 611 passes through, and the end of the second shaft portion 603 is inserted. The pin layer through hole 606 faces the inside of the enlarged diameter portion 628. The pin layer through hole 606 opens in a direction intersecting the length direction of the gap.

The annular portion 615 has two first anti-rotation recesses 616 and ten second anti-rotation recesses 617 on the inner peripheral surface. The two first anti-rotation recesses 616 are provided approximately 180° apart in the circumferential direction of the mount portion 601. The two first anti-rotation recesses 616 face each other with the center of the mount section 601 interposed therebetween. The ten second anti-rotation recesses 617 are provided five at equal angular intervals between the two first anti-rotation recesses 616 in the circumferential direction of the mount portion 601. The first anti-rotation recess 616 has a longer length in the circumferential direction of the mount portion 601 than the second anti-rotation recess 617 .

A depth gauge (not shown) can be attached to the sub-handle 600, and the knob bolt 605 is used to fix the depth gauge.

The first shaft portion 602 and the second shaft portion 603 constitute an adjustment mechanism that can adjust the length of the gap 614 within a predetermined range including a length longer than the natural length. The natural length is the length of the gap 614 in a state where no external force is applied to the mount portion 601 to widen or contract the gap 614.

The first shaft portion 602 extends in the gap length direction, and is provided on the mount portion 601 on one side (the left side in FIG. 35) of the gap 614 in the gap length direction so as to be immovable in the gap length direction. The first shaft portion 602 passes through the gap 614 and projects from the mount portion 601 to the other side in the gap length direction.

The second shaft portion 603 extends in the length direction of the gap, and is provided on the mount portion 601 on the other side of the gap 614 (on the right side in FIG. 35) in the length direction of the gap so as not to be movable in the length direction. The second shaft portion 603 projects from the mount portion 601 to the other side in the length direction.

The first shaft portion 602 and the second shaft portion 603 are engaged with each other so as to be movable relative to each other in the length direction of the gap, and the second shaft portion 603 is moved relative to the first shaft portion 602 in the length direction of the gap. The length of the gap 614 can be adjusted by.

The first and second shaft portions 603 are threadedly engaged with each other, and by rotating the second shaft portion 603 relative to the first shaft portion 602, the second shaft portion 603 is longitudinally engaged with respect to the first shaft portion 602. Relative movement is possible.

The first shaft portion 602 has a head portion 610 and a shaft portion 611 . The head 610 is located on one side of the shaft portion 611 in the gap length direction, is larger than the shaft portion 611 when viewed from the gap length direction, and has a non-circular shape, for example, a hexagonal shape. By fitting the head 610 into the head holding part 624 of the mount part 601, the first shaft part 602 cannot rotate with respect to the mount part 601, and the first shaft part 602 has a gap lengthwise from the mount part 601. It is designed to prevent it from coming off to the other side (the right side in FIG. 35). Further, a retaining ring 608 provided on the inner peripheral surface of the first cylindrical portion 612 adjacent to the head holding portion 624 allows the first shaft portion 602 to be moved from the mount portion 601 to one side in the length direction of the gap (see FIG. inside left side) It is designed so that it does not fall out.

The shaft portion 611 extends from the head 610 to the other side in the gap length direction, passes through the shaft insertion portions 626 and 627 of the mount portion 601, and reaches the inside of the second shaft portion 603. A male threaded portion 622 is provided on the outer peripheral surface of the tip portion of the shaft portion 611 .

The second shaft portion 603 has a grip portion 604, a large diameter portion 618, and a small diameter portion 619 in this order from the other side in the gap length direction.

The small diameter portion 619 is inserted into the enlarged diameter portion 628 of the second cylindrical portion 613 of the mount portion 601. Both the small diameter portion 619 and the enlarged diameter portion 628 have a circular cross section. The small diameter portion 619 has a pin insertion groove 620 and an O-ring insertion groove 621. The pin insertion groove 620 and the O-ring insertion groove 621 are groove portions that each go around the outer periphery of the small diameter portion 619. The pin insertion groove 620 is located on one side (the left side in FIG. 35) of the O-ring insertion groove 621 in the gap length direction.

A pin 607 inserted into the pin layer through hole 606 extends into the pin insertion groove 620 . The pin layer through hole 606 is located at the same position as the pin insertion groove 620 in the gap length direction. The pin 607 is inserted into the pin layer through hole 606 and extends inside the pin insertion groove 620, and moves the second shaft part 603 in the gap length direction with respect to the second cylindrical part 613 of the mount part 601. Make it impossible.

The second shaft portion 603 is rotatable relative to the second cylindrical portion 613. The O-ring 609 fits into the O-ring fitting groove 621. The O-ring 609 generates a frictional resistance force against the rotation of the second shaft part 603 with respect to the second cylindrical part 613, and suppresses the second shaft part 603 from easily rotating.

The second shaft portion 603 has a nut portion 623 that constitutes a female screw portion. The nut portion 623 is screwed into the male threaded portion 622 of the first shaft portion 602 . The nut portion 623 may be a separate part from the large diameter portion 618 and the small diameter portion 619, or may be integrated. In the example of FIG. 35, the nut portion 623 is a separate component from the large diameter portion 618 and the small diameter portion 619.

When the grip section 604 is rotated, the entire second shaft section 603 rotates integrally with respect to the mount section 601 and the first shaft section 602. Interlocking with this, the second shaft part 603 moves in the gap length direction with respect to the first shaft part 602 due to the screw engagement between the male thread part 622 of the first shaft part 602 and the nut 623 of the second shaft part 603. do. At this time, due to the engagement between the second shaft part 603 and the second cylindrical part 613 of the mount part 601 via the pin 607, the second cylindrical part 613 is moved relative to the first cylindrical part 612 in the gap length direction. Move to. This allows the length of the gap 614 to be adjusted.

If the grip part 604 is turned to the left from the state shown in FIGS. 38(B) and (E), that is, the state where the gap 614 is at its natural length, the second shaft part 603 is moved to the other side in the gap length direction (the right side in FIG. 38). ), the length of the gap 614 can be adjusted to be longer than its natural length. 38(C) and (F) show a state in which the length of the gap 614 is maximum, that is, a state in which the mount portion 601 is opened to the maximum. The length of the threaded engagement between the male threaded portion 622 of the first shaft portion 602 and the nut 623 of the second shaft portion 603 is determined so that the upper limit of the length of the gap 614 is within a predetermined length that will not damage the mount portion 601. is set.

If the grip part 604 is turned clockwise from the state shown in FIGS. 38(B) and 38(E), that is, the state where the gap 614 is at its natural length, the second shaft part 603 and the second cylindrical part 613 of the mount part 601 can be adjusted to the gap length. The length of the gap 614 can be adjusted to be shorter than its natural length by relatively moving it to one side in the width direction (left side in FIG. 35). 38(A) and (D) show a state in which the length of the gap 614 is the minimum, that is, a state in which the mount portion 601 is most closed. By adjusting the length of the gap 614 to be shorter than its natural length, the mount portion 601 can tighten the front case 340 and the sub handle 600 can be fixed to the front case 340.

By making the gap 614 wider than its natural length, the front case 340 of the working machine 1 can be passed inside the mount portion 601. The retaining convex portion 350 of the front case 340 has such a large size that it cannot be inserted inside the mount portion 601 when the gap 614 is at its natural length. The retaining convex portion 350 suppresses (prevents) the mount portion 601 from coming off forward from the front case 340 when the gap 614 is at its natural length or less than its natural length.

(Easy storage structure of sub handle 600)
To attach the sub-handle 600 to the front case 340, the mount portion 601 is fitted into the front case 340 from the front while adjusting the length of the gap 614 to be longer than its natural length. Thereafter, turn the grip portion 604 to the right to narrow the gap 614.

When attaching the sub-handle 600 to the front case 340, the attachment angle can be selected from multiple levels. Of the two first anti-rotation recesses 616 and ten second anti-rotation recesses 617 of the mount portion 601, two corresponding to the attachment angle of the sub handle 600 with respect to the front case 340 are It engages with the anti-rotation convex portion 349 in a convex-concave manner.

The circumferential length of the first anti-rotation recess 616 of the mount portion 601 is longer than the circumferential length of the anti-rotation protrusion 349 of the front case 340. The circumferential length of the second anti-rotation recess 617 of the mount portion 601 is approximately equal to the circumferential length of the anti-rotation protrusion 349 of the front case 340 .

When the second anti-rotation recess 617 of the mount portion 601 and the anti-rotation protrusion 349 of the front case 340 are engaged with each other, the sub-handle 600 can be moved without wobbling or It can be attached to the front case 340 with minimal rattling. The second anti-rotation recess 617 of the mount portion 601 is used when the sub-handle 600 is not stored, that is, when the working machine 1 is used.

When the first anti-rotation recess 616 of the mount portion 601 and the anti-rotation protrusion 349 of the front case 340 are engaged with each other, the circumferential length of the first anti-rotation recess 616 is equal to the circumferential length of the anti-rotation protrusion 349. Since the sub-handle 600 is longer than the length of the sub-handle 600, the sub-handle 600 can be rotated within a predetermined angular range with respect to the front case 340. The first anti-rotation recess 616 is used when the sub-handle 600 is stored, that is, when the working machine 1 is not in use.

39(A) to (C) are diagrams showing that the sub-handle 600 is rotatable within a predetermined angular range in the stored state.

FIG. 39(A) shows a state in which the sub-handle 600 is rotated to the maximum in the counterclockwise direction in the figure. In this state, as shown in an enlarged view in FIG. 39(B), the first detent recess 616 of the mount portion 601 and the end portions of the detent convex portion 349 of the front case 340 on one side in the circumferential direction engage with each other. This is the first engaged state.

FIG. 39(B) shows a state in which the sub-handle 600 is at the center of the rotatable range. This state is a second engaged state in which the ends of the first detent recess 616 of the mount portion 601 and the detent protrusion 349 of the front case 340 on one side in the circumferential direction do not come into contact with each other. Note that in the second engaged state, the first detent recess 616 of the mount portion 601 and the other circumferential end of the detent protrusion 349 of the front case 340 may engage with each other.

Even in the case where the first anti-rotation recess 616 of the mount part 601 and the anti-rotation protrusion 349 of the front case 340 are engaged with each other, the gap 614 of the mount part 601 can be set to a predetermined length or less shorter than the natural length. The sub handle 600 becomes unable to rotate relative to the front case 340 due to the frictional force caused by the mount portion 601 tightening the front case 340.

This embodiment has the following effects.

(1) The work machine 1 includes an output switching section 6 that switches the output (presence or absence of torque and vibration) of the output section 7 and is disposed between the output section 7 and the transmission section 5. When the transmission section 5 is removed from the output section 7, the output switching section 6 can be removed from the output section 7 toward the rear. Specifically, by removing the screw 133 and removing the gear case 140 from the front case 340 (removing the transmission section 5 from the output section 7), the output switching section 6 can be removed from the output section 7 toward the rear. Therefore, even if the spindle 470 and the chuck 500 cannot be released, the components of the output switching unit 6, such as the clutch dial 300, nut 260, clutch spring 250, etc., can be replaced, resulting in good repairability.

For comparison, consider a configuration in which the gear case 140 is extended forward, the ball bearings 335 and 461 are held, and a retaining ring prevents the clutch dial 300 from coming off forward relative to the gear case 140 (hereinafter referred to as "comparative configuration 1"). In comparative configuration 1, the retaining ring cannot be accessed unless the chuck 500 is removed from the spindle 470, and the clutch dial 300 and the like cannot be removed either forward or backward. Therefore, in comparative configuration 1, if the clutch dial 300 or the like is damaged and needs to be replaced, it is necessary to take measures such as removing the chuck 500 from the spindle 470 with a special jig or replacing the entire transmission/output component 4. This increases the time and cost required for repair. The present embodiment appropriately solves such problems.

(2) The transmitting section 5 and the output section 7 can be used in common as a module in many models, and are highly convenient.

(3) The work equipment 1 includes a transmission mechanism 50 including a final ring gear 90, a stopper block 120 that prevents the final ring gear 90 from rotating when it is in a locked position, and a stopper block 120 that urges the stopper block 120 toward the locked position. A stopper spring 117 is provided. Therefore, even if the front end of the protrusion 123 of the stopper block 120 attempting to move to the locking position comes into contact with the rear end of the outer peripheral protrusion 91 of the final ring gear 90 and cannot reach the locking position, Then, when the final ring gear 90 rotates, the outer peripheral protrusion 91 moves from the front of the protrusion 123, and the stopper block 120 automatically moves to the locking position. Therefore, it is possible to suppress the problem of not being able to make the final ring gear 90 non-rotatable, that is, the problem of not being able to shift to the drill mode.

(4) The work machine 1 can switch the position of the stopper block 120 between a locking position and a non-locking position using the clutch dial 300. Specifically, when the clutch dial 300 is rotated to the drill mode rotation position, the stopper block 120 moves to the locking position. Here, the force for moving the stopper block 120 to the locking position is the biasing force of the stopper spring 117, and is not due to the screw engagement using the rotation of the clutch dial 300. Therefore, compared to a configuration in which the stopper pin is pushed toward the final ring gear 90 by the nut 260 that moves back and forth in conjunction with the rotation of the clutch dial 300, it is easier to rotate the clutch dial 300 to the drill mode rotation position. It is easy to use and prevents problems that would otherwise occur.

(5) The stopper spring 117 is configured to urge the stopper block 120 forward, and the stopper spring 117 and the stopper block 120 are provided behind the clutch dial 300. Therefore, compared to the case where the stopper spring 117 and the stopper block 120 are provided inside the clutch dial 300, the diameter of the clutch dial 300 can be prevented from increasing, and the operability of rotating the clutch dial 300 can be prevented from deteriorating.

(6) When the clutch dial 300 is within the clutch mode rotation range, the rear stopper cam ring 210 and the front stopper cam ring 230 move from the non-locking position to the locking position against the urging force of the stopper spring 117. It functions as a regulating section that regulates the movement of the stopper block 120. Further, the rear stopper cam ring 210 and the front stopper cam ring 230 engage the stopper block 120 with the unlocked position in conjunction with the rotation of the clutch dial 300 between the drill mode rotation position and the clutch mode rotation position. It constitutes a cam mechanism that moves between the stop position and the stop position. Therefore, the back and forth movement of the stopper block 120 is limited to when the clutch dial 300 rotates between the drill mode rotational position and the clutch mode rotational position, and the screw engagement between the clutch dial 300 and the nut 260 is limited. The back and forth movement (movement between the non-locking position and the locking position) of the stopper block 120 can be suitably realized without any interference.

(7) When the clutch dial 300 rotates between the drill mode rotational position and the clutch mode rotational position, the front stopper is rotated along the outer sloped part 212 and the inner sloped part 214 of the rear stopper cam ring 210. The outer protrusion 232 and the inner protrusion 234 of the cam ring 230 move. Here, by making the inclination angles of the outer peripheral side inclined part 212 and the inner peripheral side inclined part 214 steeper than the slope of the threaded part 301 of the clutch dial 300, the threaded engagement between the clutch dial 300 and the nut 260 is Compared to the case where the stopper block 120 is moved, the stopper block 120 can be moved back and forth by a large amount in conjunction with the rotation of the clutch dial 300. As a result, the amount of operation of the clutch dial 300 required for switching between the clutch mode and the drill mode can be reduced, making it easy to use. Moreover, since the outer peripheral side inclined part 212 and the inner peripheral side inclined part 214 form a recess, the outer peripheral side protrusion 232 and the inner peripheral side protrusion 234 of the front stopper cam ring 230 can easily move in and out of the recess. Therefore, the problem of getting caught when switching between the clutch mode and the drill mode is suppressed, making it easy to use.

(8) The rear stopper cam ring 210 is located forward of the final ring gear 90, and the stopper block 120 projects forward of the final ring gear 90 and engages with the rear stopper cam ring 210. As a result, the configuration for switching to the drill mode (stopper block 120, stopper spring 117, rear stopper cam ring 210, front stopper cam ring 230) is distributed in front and behind final ring gear 90. Therefore, unlike the case where the configuration for switching to the drill mode is biased to one side of the front and rear of the final ring gear 90, it is easy to balance the radial sizes of the gear case 140 and the clutch dial 300, and the layout is efficient.

(9) In the work machine 1, when the clutch hub 370 comes to the vibration on position, the clutch hub 370 restricts the movement of the rear ratchet 410. Vibrations are generated when the front ratchet 440 is driven by the driving force of the motor 30 relative to the rear ratchet 410 whose movement is restricted. When the clutch dial 300 reaches the rotational position corresponding to the vibration mode, the outer protrusion 282 and the inner protrusion 284 of the ratchet cam ring 280 move along their own slopes 286 and 287 to the outer circumference of the clutch dial 300. The ratchet cam ring 280 and the clutch hub 370 are moved from the vibration-off position to the vibration-on position by the urging force of the ratchet spring 360 so as to enter the inside of the hole 305 and the inner circumferential recess 304 . Therefore, compared to a configuration in which the clutch hub 370 is pushed forward by a nut 260 that moves back and forth in conjunction with the rotation of the clutch dial 300, the amount of operation of the clutch dial 300 required to switch between the presence and absence of vibration is reduced. It can be reduced and is easy to use.

(10) Since the outer protrusion 282 and the inner protrusion 284 of the ratchet cam ring 280 have the inclined parts 286 and 287, the outer protrusion 282 and the inner protrusion 284 are connected to the outer hole of the clutch dial 300. 305 and the inner circumferential side recess 304 smoothly, and getting caught when switching between the drill mode and the vibration mode is suppressed, making it easy to use.

(11) When the clutch dial 300 is within the rotation range of the clutch mode and the drill mode, the ratchet cam ring 280 and the clutch dial 300 move the clutch from the vibration off position to the vibration on position against the urging force of the ratchet spring 360. It functions as a regulating section that regulates the movement of the hub 370. Additionally, the ratchet cam ring 280 and the clutch dial 300 move the clutch hub 370 between the vibration off position and the vibration on position in conjunction with the rotation of the clutch dial 300 between the vibration mode rotational position and the drill mode rotational position. A cam mechanism is configured to move between the two. Therefore, the forward and backward movement of the clutch hub 370 is limited to when the clutch dial 300 rotates between the rotational position in the vibration mode and the rotational position in the drill mode, and the clutch dial 300 and the nut 260 are not engaged with each other. The clutch hub 370 can be moved back and forth (movement between the vibration off position and the vibration on position) regardless of the situation.

(12) As shown in FIGS. 22(B) and 22(C), both circumferential sides of the locking convex portion 373 of the clutch hub 370 and the locking convex portion 412 of the rear ratchet 410 are arranged so that the clutch hub 370 is not vibrated. Inclined portions 374, 413 are provided to make it difficult to move from the vibration off position to the vibration off position. When a rotational force is applied to the rear ratchet 410 in the vibration-on position, a forward force is applied to the clutch hub 370 due to engagement between the inclined parts 374 and 413, making it difficult to move to the vibration-off position. Therefore, the clutch hub 370 is prevented from inadvertently moving to the vibration off position due to vibration or the like.

(13) Since the motor spacer 40, rear case 60, and gear case 140 are fixed with four screws 44 and constitute a highly rigid transmission housing, deformation when the clutch mechanism is operated can be suppressed. On the other hand, there is a gap between the outer surface of the rear case 60 and the two upper screws 44, and the shift arm 71 extends through the gap to the guide hole 64 of the rear case 60. Therefore, compared to a configuration in which the shift arm 71 extends in the radial direction of the rear case 60 through the outside of the screw 44 to the guide hole 64 of the rear case 60, the size of the motor accommodating portion 11 that covers the further outside of the shift arm 71 is suppressed. , it is possible to suppress the increase in size of the product.

(14) A portion of the two upper screws 44 extending in the front-rear direction on the outside of the rear case 60 is inserted into a screw collar 45 that is a cylindrical portion separate from the rear case 60. This prevents the motor spacer 40 from being bent or damaged due to over-tightening of the upper two screws 44.

(15) The front case 340 has a retaining protrusion 350 for the sub-handle 600, which prevents the sub-handle 600 from coming off forward due to vibrations during work, resulting in good workability.

(16) The sub-handle 600 has an annular mount portion 601 that has a gap 614 in a part of the circumferential direction and engages with the front case 340 of the working machine 1, and the length of the gap 614 is set to be longer than the natural length. It is configured to be adjustable within a predetermined range including the height. Therefore, even if the length of the gap 614 of the front case 340 is at its natural length and it is difficult to attach or detach it because it interferes with the retaining protrusion 350 of the front case 340, the length of the gap 614 can be adjusted to be longer than the natural length. This makes it easy to attach and detach.

(17) The first shaft part 602 and the second shaft part 603 are threadedly engaged with each other, and the length of the gap 614 can be adjusted by turning the grip part 604 provided on the second shaft part 603. Therefore, the length of the gap 614 can be easily adjusted and is convenient to use.

(18) The pin 607 extending in the pin insertion groove 620 of the second shaft portion 603 prevents the second shaft portion 603 from moving in the length direction of the gap with respect to the second cylindrical portion 613 of the mount portion 601. do. Since the pin 607 allows rotation of the second shaft portion 603, adjusting the length of the gap 614 by rotating the second shaft portion 603 is not prevented.

(19) Since the O-ring 609 generates a frictional resistance force against the rotation of the second shaft portion 603 with respect to the second cylindrical portion 613, the second shaft portion 603 is prevented from easily rotating; Good workability.

(20) Threaded engagement between the male threaded portion 622 of the first shaft portion 602 and the nut 623 of the second shaft portion 603 so that the upper limit of the length of the gap 614 is within a predetermined length that will not damage the mount portion 601. The length of is set. Therefore, damage to the mount portion 601 due to excessively widening the gap 614 can be suppressed regardless of the degree of operation by the user, making it easy to use.

(21) The mount portion 601 has a first detent recess 616 having a long circumferential length and a second detent recess 617 having a short circumferential length. When the second anti-rotation recess 617 and the anti-rotation protrusion 349 of the front case 340 are engaged with each other, the lengths in the circumferential direction of the two are approximately equal, so the sub handle 600 can be moved without rattling or with a minimum amount of movement. It can be attached to the front case 340 with ease, allowing stable work. On the other hand, when the first anti-rotation recess 616 of the mount portion 601 and the anti-rotation protrusion 349 of the front case 340 are engaged with each other, the circumferential length of the first anti-rotation recess 616 is the same as that of the anti-rotation protrusion 349. Since it is longer than the length in the circumferential direction, the sub-handle 600 can be rotated within a predetermined angle range with respect to the working machine 1 in the stored state as shown in FIGS. becomes. Therefore, the workability of storing the sub-handle 600 in the working machine 1 is good. If the storage angle cannot be moved from the angle shown in FIG. 39(C), the flange portion 625 of the grip portion 604 will interfere with the battery pack 25, battery pack mounting portion 13, etc., making storage difficult. This type of configuration can suitably solve such problems.

(22) Even if the first anti-rotation recess 616 of the mount portion 601 and the anti-rotation protrusion 349 of the front case 340 are engaged with each other, the gap 614 of the mount portion 601 is kept below a predetermined length shorter than the natural length. By doing so, the sub-handle 600 can be made unrotatable with respect to the front case 340 due to the frictional force caused by the mount portion 601 tightening the front case 340. Therefore, rattling of the sub-handle 600 in the stored state can be suppressed as necessary. Further, also when the first anti-rotation recess 616 of the mount portion 601 is configured to be used when the working machine 1 is used, rattling during operation can be suppressed.

Although the present invention has been described above using the embodiments as examples, the present invention is not limited to the embodiments. Various modifications can be made to each item specifically described in the embodiments within the scope of the claims.

In the uneven structure exemplified in the embodiment, the relationship between the depressions and the protrusions may be reversed as appropriate. For example, the rear stopper cam ring 210 may have a convex portion, and the front stopper cam ring 230 may have a concave portion that engages with the convex portion. Similarly, the ratchet cam ring 280 may have a concave portion, and the clutch dial 300 may have a convex portion that engages with the concave portion.

The number of outer circumferential convex portions 91 and stopper blocks 120 of final ring gear 90, the number of screws 44 and 133, the number of stages of set tightening torque, and the number of sub handles 600 with respect to work equipment 1, which are exemplified as specific numbers in the embodiment. The number of types of attachable angles, the number of first rotation prevention recesses 616 and second rotation prevention recesses 617, etc. do not limit the scope of the invention in any way, and can be arbitrarily changed according to required specifications.

DESCRIPTION OF SYMBOLS 1... Work equipment, 4... Transmission/output component part, 5... Transmission part, 6... Output switching part, 7... Output part, 10... Housing, 11... Motor accommodating part, 12... Handle part, 13... Battery pack mounting part , 15... Tail cover, 17... Trigger switch, 19... Forward/reverse switch, 20... Tip tool, 21... Shift knob, 23... Control board section, 25... Battery pack, 27... Screw, 30... Motor, 31... Motor shaft , 33... Ball bearing, 35... Fan, 37... Sensor board, 40... Motor spacer, 41... Bearing holding part, 42... Gear part, 43... Screw insertion hole, 45... Screw collar, 50... Transmission mechanism (deceleration mechanism) , 51... First planet gear, 53... Needle bearing, 55... First carrier, 57... Slide ring gear, 58... Groove, 60... Rear case, 61... Cylindrical part, 62... Threaded boss part, 63... Guide convex part, 64 ...Guide hole, 65...Spring holding hole, 66...Flame, 67...Through hole, 68...Left grease cover, 69...Right grease cover, 71...Shift arm, 75...Shift dog, 81...Second planetary gear, 85... Second carrier, 87... Final planetary gear, 90... Final ring gear, 91... Outer peripheral side convex part, 92... Cylindrical part, 93... Flange part, 94... Gear part, 95... Front convex part, 96... Front concave part, 101 ...Final carrier, 103...Roller, 105...Spline hub, 110...Lock ring, 115...Hub washer, 117...Stopper spring (biasing means), 120...Stopper block, 121...Base, 122...Spring holding part, 123... Locking protrusion (protrusion), 124... Wide protrusion, 131... Clutch pin, 133... Screw, 135... Spring washer, 140... Gear case, 141... Rear cylindrical part, 142... Front wall, 143... Penetration Hole, 144... Detent part, 145... Through hole, 146... Center through hole, 147... Through hole, 148... Detent part convex part, 149... Detent part convex part, 150... Front cylindrical part, 151... Screw Hole, 152... Stopper insertion groove, stopper insertion hole, 161... Pin sleeve, 165... Thrust plate, 210... Rear stopper cam ring, 211... Flat part, 212... Outer peripheral side inclined part, 213... Outer peripheral side flat part, 214... Inner circumferential side inclined part, 215... Inner circumferential side flat part, 218... Anti-rotating recess, 219... Anti-rotating recess, 230... Front stopper cam ring, 232... Outer circumferential side protrusion, 234... Inner circumferential side protruding part, 235... Engagement Stopping protrusion, 250...Clutch spring, 260...Nut, 261...Threaded part, 262...Spring locking hole, 263...Notch, 280...Ratchet cam ring, 282...Outer circumference side protrusion, 284...Inner circumference side protrusion, 285... Detent convex part, 286... Inclined part, 287... Inclined part, 288... Small protrusion, 300... Clutch dial, 301... Threaded part, 302... Locking recessed part, 304... Inner circumference side recess, 305... Outer circumference side hole Part, 306...Cylindrical part, 307...Front wall part, 308...Leaf spring mounting part, 331...Leaf spring, 335...Ball bearing (bearing), 340...Front case, 341...Large diameter cylinder part, 342...Small diameter cylinder Part, 343... Connection surface part, 344... Notch part, 345... Screw boss part, 346... Screw hole, 347... Screw hole, 348... Bearing holding part, 349... Anti-rotation convex part (rotation regulating part), 350... Removal Stopping protrusion, 351...Latching recess, 360...Ratchet spring, 370...Clutch hub, 371...Annular part, 372...Outside protrusion, 373...Locking protrusion, 374...Slanted part, 391...Thrust bearing, 395... Bearing washer, 410... Rear ratchet, 411... Uneven part (vibration generating shaped part), 412... Locking protrusion, 413... Inclined part, 431... Spring, 435... Ratchet washer, 440... Front ratchet, 441... Uneven part (Vibration generating shaped part), 461...Ball bearing, 470...Spindle, 481...O ring, 483...Retaining ring, 485...Bearing cover, 487...Through hole, 489...Screw, 495...Left-hand thread, 500...Chuck, 600 ...Sub handle, 601...Mount part, 602...First shaft part, 603...Second shaft part, 604...Grip part, 605...Knob bolt, 606...Pin layer through hole, 607...Pin, 608...Retaining ring, 609... O-ring, 610... Head, 611... Shaft, 612... First cylindrical part, 613... Second cylindrical part, 614... Gap, 615... Annular part, 616... First detent recess, 617... Second Anti-rotation recess, 618...large diameter part, 619...small diameter part, 620...pin insertion groove, 621...O ring fitting groove, 622...male thread part, 623...nut part, 624...head holding part, 625...flange part, 626... Shaft insertion part, 627... Shaft insertion part, 628... Expanded diameter part.

Claims (10)

A handle that is detachable from the work machine,
The mount part is annular and has a plurality of detent parts arranged in the circumferential direction on the inner periphery and engages with the handle attachment part of the working machine,
The plurality of detent portions are
a first detent portion having a long length in the circumferential direction;
a second detent portion having a short length in the circumferential direction;
A handle characterized by: Among the plurality of rotation prevention portions, some of the rotation prevention portions corresponding to the attachment angle of the handle with respect to the work machine engage in uneven engagement with a rotation restriction portion provided on the handle attachment portion.
A handle according to claim 1, characterized in that: The mount part has a gap in a part of the circumferential direction,
comprising an adjustment mechanism capable of adjusting the length of the gap within a predetermined range including a length longer than the natural length of the gap;
The handle according to claim 1 or 2, characterized in that: A work machine with a detachable handle,
a handle attachment part having a rotation regulating part on the outer periphery;
a handle that is annular and has a first rotation stopper on its inner circumference and has a mount portion that engages with the outer circumference of the handle attachment portion of the working machine;
The state of engagement between the first detent portion and the rotation restriction portion is as follows:
a first engaged state in which one end side ends of the first rotation stopper and the rotation restriction part in the circumferential direction are engaged with each other;
switchable between a second engagement state in which the first detent portion and the one end side end portion in the circumferential direction of the rotation restriction portion are separated from each other;
A work machine characterized by: The length in the circumferential direction of the first detent portion is longer than the length in the circumferential direction of the rotation restriction portion.
The working machine according to claim 4, characterized in that: The handle has an annular shape having a plurality of detents arranged in the circumferential direction on the inner periphery,
The plurality of detent portions are
the first detent portion;
a second detent portion having a circumferential length shorter than the first detent portion;
The working machine according to claim 4, characterized in that: Among the plurality of rotation prevention portions, some of the rotation prevention portions corresponding to the attachment angle of the handle with respect to the work machine engage in uneven engagement with the rotation restriction portion of the handle attachment portion.
The working machine according to claim 6, characterized in that: The mount part has a gap in a part of the circumferential direction,
The handle has an adjustment mechanism that can adjust the length of the gap,
The handle attachment portion has a retaining portion that prevents the mount portion from coming off from the handle attachment portion.
The working machine according to claim 4, characterized in that: The adjustment mechanism is capable of adjusting the length of the gap within a predetermined range including a length longer than the natural length of the gap,
The retaining portion prevents the mount portion from coming off from the handle attachment portion when the gap is at a natural length or less than the natural length.
The working machine according to claim 8, characterized in that: In the state in which the first rotation stopper and the rotation restriction part are engaged,
When the length of the gap is set to a predetermined length or less, the mount part cannot rotate with respect to the handle attachment part and cannot be removed in the axial direction,
When the length of the gap is longer than the predetermined length and equal to or less than the natural length, the mount part is rotatable between the first engagement state and the second engagement state with respect to the handle attachment part, and the mount part is rotatable and axially become unable to leave in the direction,
The working machine according to claim 8, characterized in that:

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