Work machine

Abstract

To provide a work machine that can suppress a defect that a ring gear cannot be brought into a non-rotatable state.SOLUTION: A work machine 1 comprises: a transmitting mechanism 50 including a final ring gear 90; a stopper block 120 that brings the final ring gear 90 into a non-rotatable state when the gear is at a locking position; and a stopper spring 117 that energizes the stopper block 120 toward the locking position. The work machine can switch, by a clutch dial 300, a position of the stopper block 120 between the locking position and an unlocking position. A rear-side stopper cam ring 210 and a front-side stopper cam ring 230 constitute a cam mechanism that moves the stopper block 120 between the unlocking position and the locking position in tandem with rotation of the clutch dial 300 between a rotating position in a drill mode and a rotating position in a clutch mode.SELECTED DRAWING: Figure 5

Description

[Technical field]

[0001] The present invention relates to a work machine. [Background technology]

[0002] The following Patent Documents 1 and 2 disclose working machines such as driver drills. The following Patent Document 3 discloses a working machine with a detachable handle.

[0003] A work machine such as a driver drill includes 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 clutch mechanism that cuts off the transmission of rotation from the transmission mechanism to the spindle at a predetermined torque.

[0004] The reduction ratio change mechanism has a shift knob operated by a user and a shift arm for moving the slide ring gear of the transmission mechanism forward and backward in response to the operation of the shift knob. The clutch mechanism has a clutch dial that allows the user to change the predetermined torque. A driver drill with a vibration function as in Patent Document 2 is also called a vibration driver drill, and the presence or absence of vibration can be switched by operating the clutch dial. [Prior art documents] [Patent documents]

[0005] [Patent Document 1] JP 2014-018914 A [Patent Document 2] JP 2015-191735 A [Patent Document 3] JP 2017-80853 A Summary of the Invention [Problem to be solved by the invention]

[0006] In a work machine such as a driver drill, the chuck and spindle are fixed with a high torque, and a special tool is required to release the fixation. In other words, without the special tool, the chuck and spindle are essentially an integrated tool holder. For this reason, it was difficult to replace parts that could not be removed without releasing the fixation between the chuck and spindle. Conventional work machines had many parts that were difficult to replace, and were difficult to repair. The first problem recognized by the present inventor was to provide a work machine that was easy to repair.

[0007] A working machine such as a driver drill can be set to a drill mode with maximum torque by fixing the ring gear of the transmission mechanism so that it cannot rotate. As a configuration for setting the mode to drill mode, a 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, when the stopper pin hits the part, the clutch dial cannot be turned, and it is not possible to switch to the drill mode, which is inconvenient to use. The second problem recognized by the present inventor is to provide a working machine that can suppress the malfunction of being unable to disable the ring gear from rotating.

[0008] In a work machine such as a driver drill, in a configuration in which a transmission mechanism is housed in multiple cases separated in the front-rear direction, the multiple cases can be fixed in the front-rear direction with fixing parts such as screws to increase the rigidity of the case and suppress deformation. Here, in a configuration in which the shift arm passes outside the fixing parts in the radial direction of the case, the product becomes large in the radial direction. The third problem recognized by the present inventor is to provide a work machine in which the size can be suppressed.

[0009] In a work machine such as a vibration driver drill, if the clutch dial operation required to switch between vibration and non-vibration is large, it takes time to switch between vibration and non-vibration, and workability is poor. The fourth problem recognized by the present inventor is to provide a work machine that can reduce the time required to switch between vibration and non-vibration.

[0010] As a configuration of a handle that can be attached to and detached from a work machine, a configuration is known in which the handle is attached to the work machine by closing the gap of an annular mount part having a gap (opening) in a part of the circumferential direction. In this configuration, if the maximum length of the gap of the mount part is the natural length, it may be difficult to attach and detach the handle. The fifth problem recognized by the present inventor is to provide a handle that is easily attached and detached to and from a work machine, and a work machine equipped with a handle that is easily attached and detached.

[0011] If the handle cannot be moved when attached to a work machine, it is not possible to finely adjust the attachment state of the handle, which can be inconvenient. A sixth problem recognized by the present inventor is to provide a handle whose attachment state to a work machine can be finely adjusted, and a work machine equipped with a handle whose attachment state can be finely adjusted.

[0012] An object of the present invention is to provide a work machine which solves at least the second of the above problems. [Means for solving the problem]

[0013] One aspect of the present invention is a work machine. A motor; a reduction mechanism having a ring gear and reducing the rotation speed of the motor; a stopper portion that is movable between a locking position and an unlocking position and prevents the ring gear from rotating when the stopper portion is in the locking position; and a biasing means for biasing the stopper portion toward the locking position.

[0014] The present invention may be expressed as an "electric operating machine", "electric tool", "electrical equipment", etc., and such expressions are also valid as aspects of the present invention. Effect of the Invention

[0015] According to the present invention, it is possible to provide a work machine which solves at least the second of the above problems. [Brief description of the drawings]

[0016] [Figure 1] 1 is a perspective view of a working machine 1 according to an embodiment of the present invention, viewed from the front side. [Diagram 2] FIG. 2 is a perspective view of the working machine 1 as seen from the rear side. [Diagram 3] FIG. [Figure 4] FIG. [Diagram 5] 2 is an enlarged right side cross-sectional view showing the configuration of a transmission / output component 4 of the work machine 1. FIG. [Figure 6] FIG. 2 is an exploded perspective view of the transmission / output component 4, as viewed from the front side. [Figure 7] FIG. 4 is an exploded perspective view of the transmission / output component 4, as viewed from the rear side. [Figure 8] 5 to 7 , (A) is a perspective view of the rear case 60 seen 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 cross-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. [Figure 9] 9(C) is a cross-sectional view taken along line AA in FIG. 9(C); FIG. 9(E) is a cross-sectional view taken along line BB in FIG. 9(C); FIG. 9(F) is a rear view of the final ring gear 90; and FIG. 9(G) is a right side view of the final ring gear 90. [Figure 10] 5 to 7, (A) to (D) are perspective views of the stopper block 120 seen from different viewpoints. (E) is a front view of the stopper block 120. (F) is a cross-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. [Figure 11] 11A is a perspective view of the gear case 140 shown in Fig. 5 to Fig. 7, (B) is a front view of the gear case 140, (C) is a cross-sectional view taken along line AA in Fig. 11B, (D) is a rear view of the gear case 140, and (E) is a right side view of the gear case 140. [Figure 12] 12(C) , (D) is a cross-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; and (G) is a right side view of the rear stopper cam ring 210. [Figure 13] 5 to 7 , (A) is a perspective view of the front stopper cam ring 230 seen 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 cross-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. [Figure 14] 14A is a perspective view of the nut 260 shown in Fig. 5 to Fig. 7, (B) is a front view of the nut 260, (C) is a cross-sectional view taken along line AA in Fig. 14B, (D) is a rear view of the nut 260, and (E) is a right side view of the nut 260. [Figure 15] 5 to 7 , (A) is a perspective view of the ratchet cam ring 280 seen 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 cross-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. [Figure 16] 16A is a perspective view of the clutch dial 300 shown in Fig. 5 to Fig. 7, seen 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 cross-sectional view taken along line AA in Fig. 16C. (E) is a rear view of the clutch dial 300. (F) is a right side view of the clutch dial 300. [Figure 17]17A is a perspective view of the front case 340 shown in Fig. 5 to Fig. 7. (B) is a front view of the front case 340. (C) is a cross-sectional view taken along line AA in Fig. 17B. (D) is a rear view of the front case 340. (E) is a right side view of the front case 340. [Figure 18] 18A is a perspective view of clutch hub 370 appearing in Figures 5 to 7, (B) is a front view of clutch hub 370, (C) is a cross-sectional view taken along line AA in Figure 18B, (D) is a rear view of clutch hub 370, and (E) is a right side view of clutch hub 370. [Figure 19] 19A is a perspective view of the rear ratchet 410 appearing in Figures 5 to 7, as viewed from the front side; (B) is a perspective view of the rear ratchet 410, as viewed from the rear side; (C) is a front view of the rear ratchet 410; (D) is a cross-sectional view taken along line AA in Figure 19C; (E) is a rear view of the rear ratchet 410; and (F) is a right side view of the rear ratchet 410. [Figure 20] 20A is a perspective view of the front ratchet 440 appearing in Figures 5 to 7, as viewed from the front side. (B) is a perspective view of the front ratchet 440, as viewed 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 cross-sectional view taken along line AA in Figure 20E. [Figure 21] 1 is a right-side cross-sectional view of the transmission / output component 4 separated into a transmission section 5, an output switching section 6, and an output section 7. FIG. [Figure 22] 22(A) is a diagram showing clutch hub 370 and rear ratchet 410 as viewed from the front. (B) is an AA cross-sectional view of Fig. 22(A) showing the positional relationship between locking protrusion 373 of clutch hub 370 and locking protrusion 412 of rear ratchet 410 in a mode other than vibration mode. (C) is an AA cross-sectional view of Fig. 22(A) showing the positional relationship between locking protrusion 373 of clutch hub 370 and locking protrusion 412 of rear ratchet 410 in vibration mode. An explanatory diagram of engagement with. [Figure 23] 4A to 4E are partially cut-away explanatory diagrams illustrating the configuration of the essential parts of the working machine 1 in the clutch mode with the set tightening torque set to the minimum, as viewed from different viewpoints. [Figure 24]4A to 4E are partially cut-away explanatory diagrams illustrating the configuration of the essential parts of the working machine 1 in the clutch mode with the set tightening torque set to the maximum, as viewed from different viewpoints. [Diagram 25] 4A to 4E are partially cut-away explanatory diagrams illustrating the configuration of the essential parts of a working machine 1 set in a drill mode, as viewed from different viewpoints. [Figure 26] 4A to 4E are partially cut-away explanatory diagrams illustrating the essential configuration of a working machine 1 set in a vibration mode, as viewed from different viewpoints. [Figure 27] FIG. 4 is a perspective view of the transmission / output component 4 as seen from the rear. [Figure 28] FIG. 4 is a left side view of the transmission / output component 4. [Figure 29] Rear view of the transmission / output component 4. [Diagram 30] 4 is a rear cross-sectional view of the transmission / output component 4, taken at an engagement portion between a shift arm 71 and a slide ring gear 57. FIG. [Diagram 31] 1 is a perspective view of an upper portion of a work machine 1 to which a sub-handle 600 is attached, as viewed from the front. [Diagram 32] 1 is a perspective view of an upper portion of the work machine 1 to which a sub-handle 600 is attached, as viewed from the rear. [Diagram 33] FIG. 2 is a front view of the work machine 1 equipped with a sub-handle 600. [Diagram 34] FIG. 2 is a front cross-sectional view of the work machine 1 equipped with a sub-handle 600. [Diagram 35] FIG. [Diagram 36] FIG. [Figure 37] FIG. 37 is an exploded perspective view of the sub-handle 600 as viewed from a different viewpoint than that of FIG. 36. [Figure 38] 6 is an explanatory diagram of the openable and closable range of a mount portion 601 of a sub-handle 600. FIG. [Figure 39] 13 is a diagram showing that the sub-handle 600 can be rotated within a predetermined angle range in a stored state. FIG. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0017] This embodiment relates to a work machine 1. The work machine 1 is a vibration driver drill. Figures 3 and 4 define the mutually orthogonal front-rear and up-down directions of the work machine 1. In addition, the left-right directions perpendicular to the front-rear and up-down directions are defined with reference to a worker facing forward.

[0018] 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 connecting the motor accommodating section 11 and the battery pack mounting section 13 perpendicularly to the front-rear direction.

[0019] 1 to 4, the work machine 1 includes a housing 10. The housing 10 is, for example, a resin molded body having a structure divided into left and right parts. The housing 10 includes a motor accommodating section 11, a handle section 12, and a battery pack mounting section 13.

[0020] The motor housing 11 is a cylindrical part whose central axis is parallel to the front-rear direction. The working machine 1 is provided with a tail cover 15 that covers the rear opening of the motor housing 11. The working machine 1 is provided with a shift knob 21 on the upper part of the motor housing 11. The shift knob 21 is a reduction ratio switching operation part that rotates a shift arm 71 that appears 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. 5. The shift arm 71 is made of, for example, metal, and corresponds to the reduction ratio switching part.

[0021] The handle portion 12 extends downward from the lower portion of the motor housing portion 11. The work machine 1 is provided with a trigger switch 17, which can switch between driving and stopping the motor 30, at the upper end portion of the handle portion 12. The work machine 1 is provided with a forward / reverse changeover switch 19, which can switch between forward and reverse rotation of the motor 30, at the boundary between the motor housing portion 11 and the handle portion 12.

[0022] The battery pack attachment section 13 is connected to the lower end of the handle section 12. A battery pack 25 that serves as the power source for the work machine 1 is detachably attached to the battery pack attachment section 13. As shown in Fig. 4, the work machine 1 includes a control board section 23 within the battery pack attachment section 13. The control board section 23 is equipped with a microcontroller that controls the drive of the motor 30, an inverter circuit for supplying current to the motor 30, and the like.

[0023] As shown in FIG. 4, the work machine 1 includes a motor 30, a fan 35, and a sensor board 37 in the motor housing 11. The motor 30 is, for example, an inner rotor type brushless motor, and is driven by 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 (a portion of the motor 30 excluding the motor shaft 31), rotates integrally with the motor shaft 31, and generates cooling air that cools 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.

[0024] (Configuration of transmission / output component 4) 5 to 20 relate to the configuration of the transmission / output component 4 (transmission / output unit) of the work machine 1, that is, the configuration of the portion forward of the motor 30. FIG.

[0025] The transmission / output component 4 includes a motor spacer 40 serving as a lid for the first case.

[0026] As shown in FIGS. 6 and 7, the motor spacer 40 has a bearing holder 41, a gear portion 42, and four screw insertion holes 43.

[0027] The bearing holder 41 is located at the rear center of the motor spacer 40. As shown in FIG. 4 , the bearing holder 41 holds a ball bearing 33 (bearing) that supports the front part of the motor shaft 31. The gear portion 42 is provided on the inner circumferential surface of the motor spacer 40. That is, the motor spacer 40 functions as a first-stage ring gear of the transmission mechanism 50.

[0028] The four screw insertion holes 43 are through holes for passing screws 44 through. The screws 44 are fixing parts that fix the motor spacer 40 and the rear case 60 to the gear case 140. The upper two screws 44 correspond to a first fixing part, and the lower two screws 44 correspond to a second fixing part. The screws 44 extend in the front-rear direction. The screw collar 45 shown in Figs. 6 to 7 is made of, for example, metal, and is a member through which the upper two screws 44 pass.

[0029] The transmission / output structure 4 includes a rear case 60 serving as a cylindrical first case. The rear case 60 is made of, for example, resin.

[0030] As shown in FIGS. 8(A) to (G), the rear case 60 has a cylindrical portion 61, two screw boss portions 62 as insertion portions, a guide protrusion portion 63, a guide hole 64, a spring retaining hole 65, a flange portion 66, and two through holes 67.

[0031] The tubular portion 61 is a cylindrical portion coaxial with the motor shaft 31. The screw boss portions 62 are provided at the left and right lower portions of the tubular portion 61 so as to protrude radially outward. The through hole 67 passes through the screw boss portion 62 in the front-rear direction. The through hole 67 is a portion through which the two lower screws 44 shown in Figures 6 and 7 are passed.

[0032] The guide protrusion 63 functions as a rotation guide for the shift arm 71. The guide hole 64 is a long through hole (groove-shaped hole) through which the shift arm 71 passes, and serves as a guide for the movement of the lower part of the shift arm 71 in the front-rear direction. The spring retaining hole 65 is a non-through hole that opens to the front surface of the flange 66 and retains the rear end of the stopper spring 117 that appears in Figs. 5 to 7. The flange 66 spreads outward in the radial direction from the front end of the cylindrical part 61.

[0033] The left grease cover 68 and the right grease cover 69 shown in Figures 6 to 7 are made of, for example, resin, 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 each function as a space to store lubricating oil that leaks out from the guide holes 64.

[0034] The transmission / output component 4 includes a final ring gear 90. The final ring gear 90 is made of, for example, metal.

[0035] As shown in FIGS. 9(A) to (G), the final ring gear 90 has six outer circumferential side convex portions 91 (projections), a cylindrical portion 92, a flange portion 93, a gear portion 94, six front convex portions 95, and six front concave portions 96.

[0036] The cylindrical portion 92 is a cylindrical portion coaxial with the motor shaft 31. The flange portion 93 extends radially outward from the front end portion of the cylindrical portion 92. The six outer peripheral side protrusions 91 are arranged at equal angular intervals in the circumferential direction, and each protrudes radially outward from the front portion of the outer peripheral surface of the cylindrical portion 92. The outer peripheral side protrusions 91 are provided straddling the front portion of the outer peripheral surface of the cylindrical portion 92 and the back surface of the flange portion 93. The gear portion 94 is provided on the inner peripheral surface of the cylindrical portion 92.

[0037] The front convex portion 95 and the front concave portion 96 are provided on the front surface of the flange portion 93. The six front concave portions 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 against the front concave portions 96.

[0038] The transmission / output component 4 includes a stopper block 120 as a stopper portion. The stopper block 120 is made of, for example, metal.

[0039] As shown in FIGS. 10(A) to (H), the stopper block 120 has a base portion 121, a spring holding portion 122, a locking protrusion 123, and a wide protrusion .

[0040] The base 121 is a planar portion (plate-shaped portion) that fits 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 121, and holds the front end portion of the stopper spring 117 that appears in FIGS. 5 to 7. The base 121 is located between the inner circumferential surface of the gear case 140 and the outer circumferential surface of the final ring gear 90.

[0041] The locking protrusion 123 is provided on one surface of the base 121, which surface faces the outer circumferential surface of the final ring gear 90. The locking protrusion 123 is a protrusion that engages with an outer circumferential side protrusion 91 of the final ring gear 90 when in an locking position described below, thereby rendering the final ring gear 90 unrotatable.

[0042] The wide protrusion 124 is connected to the rear of the locking protrusion 123. The wide protrusion 124 has a circumferential width greater than that of the locking protrusion 123. The wide protrusion 124 is provided to form the spring retaining hole 122.

[0043] The transmission / output component 4 includes a gear case 140 serving as a second case. The gear case 140 is made of, for example, metal.

[0044] As shown in Figures 11(A) to (E), gear case 140 has a rear cylindrical portion 141, a front wall portion 142, six through holes 143, three anti-rotation portions 144, three through holes 145, a central through hole 146, four through holes 147, anti-rotation portion protrusions 148, 149, a front cylindrical portion 150, four screw holes 151, three stopper insertion grooves 152, and three stopper insertion holes 153.

[0045] 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 work machine 1. The front wall portion 142 connects a front portion of the rear cylindrical portion 141 and a rear portion of the front cylindrical portion 150, and extends to the radially inner side of the front cylindrical portion 150. Six through holes 143 penetrate the front wall portion 142 in the front-rear direction on the radially outer side of the front cylindrical portion 150, and each hold a pin sleeve 161 (made of, for example, metal) that appears in Figures 6 to 7.

[0046] The three anti-rotation portions 144 are arranged at equal angular intervals in the circumferential direction, and each protrudes forward from the front end of the front cylindrical portion 150. The anti-rotation portions 144 sandwich anti-rotation protrusions 285 of a ratchet cam ring 280 (described later) from both circumferential sides, preventing the ratchet cam ring 280 from rotating.

[0047] 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 holes 145 are portions through which the screws 133 appearing in Figs. 5 to 7 pass, and correspond to the transmission unit housing side mounting portion. The spring washers 135 appearing in Figs. 6 to 7 are made of metal, for example, and are interposed between the heads of the screws 133 and the periphery of the through holes 145 to prevent the screws 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 appearing in Fig. 1 pass, that is, the screws 27 for fixing the gear case 140 to the motor accommodating portion 11 from the front.

[0048] Anti-rotation convex portions 148, 149 are protrusions that engage (fit) with anti-rotation concave portions 218, 219 of rear stopper cam ring 210 described below to prevent rear stopper cam ring 210 from rotating. Front cylindrical portion 150 is a cylindrical portion that is coaxial with motor shaft 31 and has a smaller diameter than rear cylindrical portion 141. Four screw holes 151 are portions into which screws 44 appearing in Figures 6 to 7 are screwed.

[0049] The three stopper insertion grooves 152 are recessed grooves that are provided at equal angular intervals in the circumferential direction on the inner circumferential surface of the rear cylindrical portion 141 and extend in the front-rear direction. The base portion 121 of the stopper block 120 fits into each of the stopper insertion grooves 152. The stopper block 120 is guided by the stopper insertion grooves 152 to move in the front-rear direction.

[0050] 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 blocks 120 can protrude forward from the front wall portion 142 by penetrating each of the stopper insertion holes 153.

[0051] The motor spacer 40, rear case 60, and gear case 140 are assembled together by four screws 44 to form a transmission housing that accommodates the transmission mechanism 50.

[0052] The transmission mechanism 50 is a reduction mechanism made up of a planetary gear mechanism, and includes the gear portion 42 of the motor spacer 40, a first planetary gear 51, a first carrier 55, a slide ring gear 57, a second planetary gear 81, a second carrier 85, a final planetary gear 87, a final ring gear 90, and a final carrier 101. These components constituting the transmission mechanism 50 are made of, for example, metal.

[0053] The needle bearing 53 shown in FIGS. 6 and 7 is interposed between the inner circumferential surface of the first planetary gear 51 and a pin that protrudes rearward from the first carrier 55.

[0054] The slide ring gear 57 has a groove 58 that engages with the end of the shift arm 71. The slide ring gear 57 moves back and forth in response to the forward and backward movement of the end of the shift arm 71 accompanying the rotation of the shift arm 71.

[0055] When positioned forward, the slide ring gear 57 meshes with the second planetary gear 81. At this time, the slide ring gear 57 is fixed unrotatably by a shift dog 75 (made of metal, for example), and the transmission mechanism 50 has a high reduction ratio with three speed reduction stages.

[0056] When the slide ring gear 57 is positioned at the rear, it meshes with both the first planetary gear 51 and the second planetary gear 81. At this time, the transmission mechanism 50 has a low reduction ratio with two-stage reduction.

[0057] 5 to 7 is made of, for example, metal, and is a component that meshes with the inner peripheral portion of the final carrier 101 and the outer peripheral portion at the rear end of the spindle 470 to transmit the rotation of the final carrier 101 to the spindle 470. The final carrier 101 is made of, for example, metal.

[0058] 6 and 7 are made of metal, for example, and are components for suppressing the transmission of rotation from the spindle 470 and chuck 500 side to the final carrier 101 side. When an attempt is made to rotate the chuck 500, the roller 103 is sandwiched and fixed between the outer periphery of the spline hub 105 and the inner periphery of the lock ring 110. The respective components are positioned such that the roller 103 is not fixed when the rotation is transmitted from the final carrier 101 side to the spindle 470 and chuck 500 side.

[0059] Hub washer 115 shown in Figures 6 and 7 is made of, for example, metal and is a part that is interposed between the front surface of splined hub 105 and the back surface of front wall portion 142 of gear case 140 to prevent contact between gear case 140 and splined hub 105 and reduce friction.

[0060] The transmission / output component 4 includes a rear stopper cam ring 210 serving as a first cam.

[0061] The rear stopper cam ring 210 is located forward of the stopper block 120 and contacts the front end of the stopper block 120, and is biased forward by the stopper spring 117 via the stopper block 120, thereby restricting rotation relative to the gear case 140.

[0062] As shown in FIGS. 12(A) to (G), rear stopper cam ring 210 includes a flat portion 211, an outer peripheral inclined portion 212, an outer peripheral flat portion 213, an inner peripheral inclined portion 214, an inner peripheral flat portion 215, and anti-rotation recesses 218 and 219.

[0063] The flat portion 211 is a planar portion perpendicular to the front-rear direction and provided on the front surface of the rear stopper cam ring 210. The outer peripheral side 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 portion 212 has one end connected to the flat portion 211 and is an inclined surface inclined from the flat portion 211 so as to move more rearward as it proceeds clockwise in a front view. The outer peripheral side flat portion 213 is a planar portion perpendicular to the front-rear direction and extends circumferentially from the other end of the outer peripheral side inclined portion 212. The outer peripheral side inclined portion 212 and the outer peripheral side flat portion 213 form a recess or a hole.

[0064] The inner circumferential inclined portion 214 is provided on a radially inner portion of the front surface of the rear stopper cam ring 210. The inner circumferential inclined portion 214 is located approximately 180° away from the outer circumferential inclined portion 212 in the circumferential direction. The inner circumferential inclined portion 214 has one end connected to the flat portion 211 and is an inclined surface that is inclined from the flat portion 211 so as to move more rearward as it proceeds clockwise when viewed from the front. The inner circumferential flat portion 215 is a flat portion that is perpendicular to the front-to-rear direction and extends circumferentially from the other end of the inner circumferential inclined portion 214. The inner circumferential inclined portion 214 and the inner circumferential flat portion 215 form a recess or a hole.

[0065] The anti-rotation recesses 218 , 219 engage (fit) with the anti-rotation protrusions 148 , 149 of the gear case 140 described above, rendering the rear stopper cam ring 210 non-rotatable relative to the gear case 140 .

[0066] 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, for example, resin.

[0067] 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 .

[0068] As shown in FIGS. 13(A) to 13(G), the front stopper cam ring 230 has an outer circumferential side protrusion 232, an inner circumferential side protrusion 234, and two locking protrusions 235. As shown in FIG.

[0069] The outer peripheral projection 232 projects rearward from the radially outer portion of the front stopper cam ring 230. The outer peripheral projection 232 is a flat or curved plate-like portion that is approximately perpendicular to the radial direction. The radial position of the outer peripheral projection 232 is equal to the radial positions of the outer peripheral inclined portion 212 and the outer peripheral flat portion 213 of the rear stopper cam ring 210.

[0070] The inner circumferential projection 234 projects rearward from a radially inner portion of the front stopper cam ring 230. The inner circumferential projection 234 is a flat or curved plate-like portion that is approximately perpendicular to the radial direction. The inner circumferential projection 234 is located approximately 180° away from the outer circumferential projection 232 in the circumferential direction. The radial position of the inner circumferential projection 234 is equal to the radial positions of the inner circumferential inclined portion 214 and the inner circumferential flat portion 215 of the rear stopper cam ring 210.

[0071] The two locking protrusions 235 protrude forward from the radially outer portion of the front stopper cam ring 230 at positions spaced apart by approximately 180° in the circumferential direction. The locking protrusions 235 are flat or curved plate-like portions that are substantially perpendicular to the radial direction. The locking protrusions 235 engage (fit) with locking recesses 302 of the clutch dial 300, which will be described later. This allows the front stopper cam ring 230 to rotate together with the clutch dial 300.

[0072] The transmission / output component 4 includes a nut 260 as a screw member. The nut 260 is made of, for example, resin.

[0073] As shown in FIGS. 14(A) to (E), the nut 260 has a threaded portion 261, six spring locking holes 262, and three notches 263.

[0074] The threaded portion 261 is provided on the outer peripheral surface of the nut 260, and screws into a threaded portion 301 of the clutch dial 300 described below. The six spring locking holes 262 are non-through holes arranged at equal angular intervals in the circumferential direction, and each holds a front end portion of the clutch spring 250 (made of metal, for example) shown in Figures 5 to 7. The three cutout portions 263 are arranged at equal angular intervals in the circumferential direction, and each passes through a screw 133 shown in Figures 5 to 7.

[0075] 6 and 7 is made of, for example, metal, and is urged rearward against nut 260 by clutch spring 250, pressing the front end of clutch pin 131 rearward to press the rear end of clutch pin 131 against the front surface of final ring gear 90. Clutch pin 131 is made of, for example, metal, and extends in the front-rear direction through pin sleeve 161 held in through hole 143 of gear case 140 described above.

[0076] The transmission / output component 4 includes a cam ring, namely, a ratchet cam ring 280. The ratchet cam ring 280 is made of, for example, metal.

[0077] As shown in FIGS. 15(A) to (G), ratchet cam ring 280 has an outer circumferential side protrusion 282, an inner circumferential side protrusion 284, three anti-rotation protrusions 285, and three small protrusions 288.

[0078] The outer peripheral projection 282 projects forward from a radially outer portion of the ratchet cam ring 280. The outer peripheral projection 282 is a flat or curved plate-like portion that is approximately perpendicular to the radial direction.

[0079] The inner peripheral projection 284 projects forward from a radially inner portion of the ratchet cam ring 280. The inner peripheral projection 284 is a flat or curved plate-like portion that is approximately perpendicular to the radial direction.

[0080] 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 protrusions 285 are sandwiched in the gaps of the two-pronged anti-rotation portions 144 of the gear case 140 described above. This makes it impossible for the ratchet cam ring 280 to rotate relative to the gear case 140. The back surface of the anti-rotation protrusions 285 comes into contact with the front surface of an outer protrusion 372 of the clutch hub 370 described below, and is pressed forward.

[0081] The three small protrusions 288 each protrude radially inward at a position spaced a predetermined angle in the circumferential direction from the anti-rotation protrusion 285. The small protrusions 288 come into contact with the outer circumferential surface of a screw boss portion 345 of the front case 340 (described later) at a point where the circumferential position of the anti-rotation protrusion 285 coincides with the circumferential position of an outer protrusion 372 of the clutch hub 370, and play a role in circumferential positioning.

[0082] 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 gap in the circumferential direction between the anti-rotation protrusion 285 and the small protrusion 288. Then, the ratchet cam ring 280 is rotated until the small protrusion 288 contacts the outer circumferential surface of the threaded boss portion 345 of the front case 340, and the biasing force of the ratchet spring 360 brings the back surface of the anti-rotation protrusion 285 into contact with the front surface of the outer protrusion 372 of the clutch hub 370.

[0083] The transmission / output component 4 includes a clutch dial 300 as a switching operation part. The clutch dial 300 is made of, for example, resin.

[0084] As shown in FIGS. 16(A) to (F), the clutch dial 300 has a threaded portion 301, two locking recesses 302, an inner peripheral recess 304, an outer peripheral hole 305, a cylindrical portion 306, a front wall portion 307, and a leaf spring attachment portion 308.

[0085] The cylindrical portion 306 has a central axis coaxial with the motor shaft 31, a cross section perpendicular to the front-rear direction is generally circular, and a diameter thereof decreases toward the front. The front wall portion 307 extends radially inward from the front end portion of the cylindrical portion 306.

[0086] The threaded portion 301 is provided on the inner peripheral surface of the cylindrical portion 306. The threaded portion 301 screws into 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 described below 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.

[0087] The two locking recesses 302 are located at positions spaced apart from each other by approximately 180° in the circumferential direction, and are each formed as a notch by partially cutting out the lower end of the threaded portion 301. The locking recesses 302 engage with the locking protrusions 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.

[0088] The inner recess 304 is located on the radially inner portion of the back surface of the front wall portion 307. The radial position of the inner recess 304 is equal to the radial position of the inner protrusion 284 of the ratchet cam ring 280 described above (or includes the radial position range of the inner protrusion 284).

[0089] The outer periphery side hole 305 penetrates in the front-rear direction through a radially outer portion of the front wall portion 307. The radial position of the outer periphery side hole 305 is equal to the radial position of the outer periphery side protrusion 282 of the ratchet cam ring 280 described above (or includes the radial position range of the outer periphery side protrusion 282).

[0090] The leaf spring attachment portion 308 is a portion for attaching a leaf spring 331 (made of metal, for example) which appears in FIGS.

[0091] The transmission / output component 4 includes a front case 340 serving as an output unit housing. The front case 340 is made of, for example, metal.

[0092] As shown in Figures 17(A) to (E), front case 340 has large diameter cylindrical portion 341, small diameter cylindrical portion 342, connection surface portion 343, three notches 344, three screw boss portions 345, three screw holes 346, three screw holes 347, bearing holder 348, two anti-rotation protrusions 349, two anti-dislodgement protrusions 350, and locking recess 351.

[0093] 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 rearward 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 disposed within the small diameter cylindrical portion 342. The connection surface portion 343 is a wall portion perpendicular to the front-rear 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.

[0094] The three notches 344 are arranged at equal angular intervals in the circumferential direction, and each of them receives an outer protrusion 372 of clutch hub 370 described below. The three screw bosses 345 are arranged at equal angular intervals in the circumferential direction, and each of them protrudes radially outward from the outer circumferential surface of small diameter cylindrical portion 342. The three screw holes 347 are blind holes that open to the back surface of screw boss portion 345, and each of them receives a screw 133 shown in Figures 5 to 7. Screw boss portion 345 and screw hole 347 correspond to an output portion housing side mounting portion.

[0095] The three screw holes 346 are blind holes that open to the front surface of the connection surface portion 343, and screws 489, which appear in Figs. 5 to 7, are screwed into the three screw holes 346. The three screw holes 346 are provided at the same positions in the circumferential direction as the three screw holes 347. The bearing holder 348 holds the ball bearing 335 (bearing), which appears in Figs. 5 to 7. The ball bearing 335 is made of, for example, metal, and supports the rear portion of the spindle 470 so that it can rotate freely.

[0096] The two anti-rotation protrusions 349 are located at positions spaced apart from each other by approximately 180° in the circumferential direction, and respectively protrude radially outward from the left and right parts of the outer circumferential surface of the large diameter cylinder portion 341. The anti-rotation protrusions 349 are rotation restricting portions that engage (fit) with a first anti-rotation recess 616 or a second anti-rotation recess 617 of the sub-handle 600 described below, and restrict the rotation of the sub-handle 600 relative to the front case 340.

[0097] The two anti-slip protrusions 350 are located at positions spaced apart from each other by approximately 180° in the circumferential direction, and protrude radially outward from the left and right parts of the outer circumferential surface of the large diameter cylindrical portion 341, respectively. The protruding length of the anti-slip protrusions 350 is shorter than the protruding length of the anti-rotation protrusions 349. The anti-slip protrusions 350 are continuous with the anti-rotation protrusions 349 on both sides in the circumferential direction. The anti-slip protrusions 350 prevent the sub-handle 600, described below, from slipping out (detaching) forward from the front case 340.

[0098] The locking recesses 351 are grooves into which the leaf springs 331 fit, and there are locking recesses 351 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. By fitting the leaf springs 331 into the locking recesses 351, the rotational position of the clutch dial 300 is determined, and the clutch dial 300 is locked in the rotational direction to prevent it from rotating inadvertently.

[0099] The transmission / output component 4 includes a clutch hub 370 .

[0100] The clutch hub 370 is a restricting portion that restricts, in the vibration mode, the movement (rotation) of the rear ratchet 410. The clutch hub 370 is made of, for example, metal.

[0101] As shown in FIGS. 18(A) to (E), the clutch hub 370 has an annular portion 371, three outer protrusions 372, and six locking protrusions 373.

[0102] 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 protrusions 373 are arranged at equal angular intervals in the circumferential direction, and each protrudes radially inward from a rear portion of the inner circumferential surface of the annular portion 371.

[0103] The transmission / output component 4 includes a rear ratchet 410 as a second vibration part. The rear ratchet 410 is made of, for example, metal.

[0104] 19(A) to 19(F), rear ratchet 410 is ring-shaped, has uneven portions 411 on the front surface, and has six locking protrusions 412 on the front portion of the outer circumferential surface. The six locking protrusions 412 are arranged at equal angular intervals in the circumferential direction, and are each a protrusion that protrudes radially outward.

[0105] 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 it, and receive a load in the front-rear direction. The thrust bearing 391 and the bearing washer 395 reduce friction and suppress power loss when the tool bit 20 is pressed against a mating material.

[0106] The transmission / output component 4 includes a front ratchet 440 as a first vibration part. The front ratchet 440 is made of, for example, metal.

[0107] 20(A) to 20(F), the front ratchet 440 is ring-shaped and has an uneven portion 441 on its back surface. The uneven portion 441 is a vibration generating portion that outputs vibration to the spindle 470 by coming into contact with the uneven portion 411 (vibration generating portion) of the rear ratchet 410 and rotating relatively.

[0108] 5 to 7 is made of, for example, metal, and biases the front ratchet 440 forward relative to the rear ratchet 410. As a result, when the tool bit 20 is not pressed against a mating member, the rear ratchet 410 and the front ratchet 440 are not in contact with each other, and the generation of vibration is suppressed. The ratchet washer 435 is made of, for example, metal, and prevents contact between the front ratchet 440 and the spring 431, thereby reducing friction.

[0109] 5 to 7 is made of, for example, metal, and rotatably supports the front ratchet 440 and the middle portion of the spindle 470 with respect to the front case 340. The front ratchet 440 rotates integrally with the spindle 470.

[0110] The transmission / output component 4 includes a spindle 470 and a chuck 500. The spindle 470 and the chuck 500 are both made of, for example, metal. The spindle 470 is rotationally driven by the motor 30 via the transmission mechanism 50. The chuck 500 holds the tool bit 20 shown in FIG. 3 and rotates together with the spindle 470.

[0111] A threaded portion on the inner peripheral surface of the rear of the chuck 500 is screwed into a threaded portion on the outer peripheral surface of the front of the spindle 470, thereby fixing the chuck 500 to the spindle 470. The chuck 500 is also fixed to the spindle 470 by a left-handed screw 495 (made of, for example, metal). The spindle 470 and the chuck 500 are firmly fixed to each other and substantially constitute an integrated tool holder.

[0112] Bearing cover 485 shown in FIGS. 5 to 7 is made of, for example, metal, and is fixed to front case 340 by screws 489 which pass through through holes 487 provided in bearing cover 485 and are screwed into screw holes 346 of front case 340.

[0113] O-ring 481 shown in Fig. 5 to Fig. 7 is an elastic body such as rubber, and is provided between the inner peripheral surface of bearing cover 485 and the outer peripheral surface of spindle 470. O-ring 481 slides on the inner peripheral surface of bearing cover 485, and reduces the impact when the rotation is stopped (when braking). O-ring 481 also has the function of preventing oil leakage.

[0114] 5 to 7 is made of, for example, metal, and is provided on the inner circumferential surface of small diameter cylindrical portion 342 of front case 340 and functions to prevent ball bearing 461 from falling off.

[0115] (Disassembly of transmission / output component 4) FIG. 21 is a right-side cross-sectional view of the transmission / output component 4 separated into the transmission section 5, the output switching section 6, and the output section 7. As shown in FIG.

[0116] 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 unit 5 includes a transmission unit housing (motor spacer 40, rear case 60, gear case 140) and each part (transmission mechanism 50, etc.) held or supported therein.

[0117] The output switching unit 6 switches the output of the output unit 7, i.e., torque and the presence or absence of vibration. The output switching unit 6 is disposed to be sandwiched between the output unit 7 and the transmission unit 5 in the front-rear direction. The output switching unit 6 includes a clutch dial 300 and various parts (such as a nut 260) held or supported thereby.

[0118] The output section 7 includes a front case 340 and each of the parts held or supported thereby, that is, a spindle 470, a chuck 500, ball bearings 335 and 461, and the like.

[0119] The transmission unit 5 is detachably assembled to the output unit 7 from the rear side. Specifically, the gear case 140 is assembled to the front case 340 from the rear side by screws 133 that pass through through holes 145 of the gear case 140 and are screwed into screw holes 347 of the front case 340.

[0120] The screw 133 is an example of a fixing part that fixes the output unit 7 and the transmission unit 5. The range of the screw 133 and the output switching unit 6 at least partially overlap. When the fixation by the screw 133 is released, the transmission unit 5 can be removed from the output unit 7.

[0121] When the transmission unit 5 is removed from the output unit 7, that is, when the screws 133 are removed and the gear case 140 is removed from the front case 340, the output switching unit 6 can be removed rearward from the output unit 7 while the spindle 470 and chuck 500 remain fixed.

[0122] (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.

[0123] The clutch mode is a mode in which the transmission of rotation from the transmission mechanism 50 to the spindle 470 is interrupted when the set tightening torque (predetermined torque) is exceeded, i.e., a mode in which the clutch mechanism is active. The set tightening torque can be adjusted in multiple steps, for example, in 22 steps, by operating the clutch dial 300.

[0124] Figures 23(A)-(E) show the clutch mode with the set tightening torque set to the minimum, and Figures 24(A)-(E) show the clutch mode with the set tightening torque set to the maximum.

[0125] The clutch mechanism stops the rotation of the final ring gear 90 up to a set tightening torque, but allows the rotation of the final ring gear 90 once the tightening torque reaches or exceeds the set tightening torque. The clutch mechanism includes a nut 260, a clutch spring 250, a thrust plate 165, and a clutch pin 131.

[0126] When a load (torque) is applied to the tool bit 20 while the motor 30 is running, the free final ring gear 90 tries to rotate. The clutch pin 131 is positioned in the front recess 96 of the final ring gear 90 until the set tightening torque is reached. This makes the final ring gear 90 unable to rotate, and torque transmission by the transmission mechanism 50 becomes effective.

[0127] On the other hand, when the torque applied to the tool bit 20 increases and exceeds the set tightening torque, in other words, when a load (torque) greater than 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 is applied to the final ring gear 90, the final ring gear 90 rotates and the clutch pin 131 overcomes the front convex portion 95 of the final ring gear 90. This is the clutch operation, and the torque transmission by the transmission mechanism 50 is interrupted by the clutch mechanism.

[0128] 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.

[0129] 23(A)-(E), nut 260 is in the most advanced position, and the amount of compression of clutch spring 250 is minimal (set tightening torque is the lowest). When nut 260 is rotated clockwise from this state as viewed from the front, nut 260 moves backward, and the amount of compression of clutch spring 250 increases. In the states of Figures 24(A)-(E), nut 260 is in the most advanced position, and the amount of compression of clutch spring 250 is maximum (set tightening torque is maximum).

[0130] (Drill mode switching configuration) The drill mode is a mode in which the final ring gear 90 is rendered unrotatable without using a clutch mechanism, and is a mode in which the work machine 1 can produce a maximum tightening torque.

[0131] From the state shown in Figures 24(A) to (E), i.e., the clutch mode and the set tightening torque is set to the maximum, when the clutch dial 300 is further rotated clockwise as viewed from the front to a rotation position corresponding to the drill mode, the state changes to that shown in Figures 25(A) to (E), i.e., the drill mode.

[0132] The structure 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.

[0133] The stopper block 120 is movable between a locking position (advance position) and an unlocking position (retracted position) and disables the rotation of the final ring gear 90 when in the locking position. The front end of the stopper block 120 protrudes forward beyond the final ring gear 90. The stopper spring 117 is made of, for example, metal and biases the stopper block 120 forward, i.e., toward the locking position.

[0134] The clutch dial 300 is a switching operation unit that can switch the position of the stopper block 120 between an engaged position and an unengaged position. The clutch dial 300 is located in front of the final ring gear 90. The clutch dial 300 is rotatable around an extension of the axis of the motor shaft 31.

[0135] The rear stopper cam ring 210 and the front stopper cam ring 230 are restriction 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. The restriction by the rear stopper cam ring 210 and the front stopper cam ring 230 can be switched between on and off by operating the clutch dial 300. In other words, 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.

[0136] The rear stopper cam ring 210 is located on the front side of the stopper block 120, and its back surface comes into contact with the stopper block 120. The rear stopper cam ring 210 comes into contact with the stopper block 120 on the outer side of the final ring gear 90 in the radial direction of the final ring gear 90. The rear stopper cam ring 210 is located forward of 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 relative to the gear case 140 is restricted by the engagement (fitting) of the rotation stopper protrusions 148, 149 of the gear case 140 and the rotation stopper recesses 218, 219 of the rear stopper cam ring 210.

[0137] Front stopper cam ring 230 is located forward of rear stopper cam ring 210. Due to engagement (fitting) between locking protrusion 235 of front stopper cam ring 230 and locking recess 302 of clutch dial 300, front stopper cam ring 230 rotates together with clutch dial 300. When clutch dial 300 reaches a rotation position corresponding to the drill mode, that is, when front stopper cam ring 230 reaches a predetermined rotation position, rear stopper cam ring 210 moves forward. This releases the restriction on movement of stopper block 120 from the non-locking position to the locking position.

[0138] The rear stopper cam ring 210 has an outer peripheral inclined portion 212 and an outer peripheral flat portion 213 as recesses, and an inner peripheral inclined portion 214 and an inner peripheral flat portion 215 as recesses. The front stopper cam ring 230 has an outer peripheral protrusion 232 and an inner peripheral protrusion 234 as protrusions. In the process of the front stopper cam ring 230 coming to a predetermined rotation position (the process of the clutch dial 300 coming to a rotation position for the drill mode), the outer peripheral protrusion 232 and the inner peripheral protrusion 234 descend the outer peripheral inclined portion 212 and the inner peripheral inclined portion 214, and the rear stopper cam ring 210 moves forward. The inclination of the outer peripheral inclined portion 212 and the inner peripheral inclined portion 214 is preferably steeper than the inclination of the thread portion 301 of the clutch dial 300.

[0139] 24(A)-(E) and 25(A)-(E) show how, in the process of switching from the clutch mode to the drill mode, the outer peripheral projection 232 of the front stopper cam ring 230 descends the outer peripheral inclined portion 212 of the rear stopper cam ring 210, the rear stopper cam ring 210 advances due to the bias of the stopper spring 117, and the stopper block 120 moves to the locking position (advance position). In the drill mode, the locking protrusion 123 of the stopper block 120 in the locking position engages (abuts in the rotational direction) with the outer peripheral protrusion 91 of the final ring gear 90 to disable the rotation of the final ring gear 90. Note that the locking protrusion 123 of the stopper block 120 in the non-locking position does not engage with the outer peripheral protrusion 91 of the final ring gear 90, allowing the final ring gear 90 to rotate.

[0140] When clutch dial 300 is within a specified rotation range corresponding to the aforementioned clutch mode (a rotational position between the states of Figures 23(A) to (E) and Figures 24(A) to (E)), outer circumferential protrusion 232 and inner circumferential protrusion 234 of front stopper cam ring 230 abut against flat portion 211 of rear stopper cam ring 210, so that rear stopper cam ring 210 does not move forward and stopper block 120 does not move to the engaging position.

[0141] (Vibration mode switching configuration) The vibration mode is a mode in which back and forth vibration is applied to the spindle 470 in the drill mode.

[0142] When the clutch dial 300 is further rotated clockwise as viewed from the front from the state shown in Figures 25(A) to (E), i.e., the drill mode, to a rotation position corresponding to the vibration mode, it enters the state shown in Figures 26(A) to (E), i.e., the vibration mode.

[0143] The configuration for switching to the 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 .

[0144] The rear ratchet 410 and the front ratchet 440 are vibration units 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.

[0145] The ratchet cam ring 280 and the clutch hub 370 are a vibration switching part that moves from a vibration-off position (retracted position) to a vibration-on position (forward position) in response to the operation of the clutch dial 300. The ratchet spring 360 is made of, for example, metal, and is a biasing part that biases the ratchet cam ring 280 and the clutch hub 370 forward, i.e., toward the vibration-on position.

[0146] The outer peripheral protrusion 282 and inner peripheral protrusion 284 of ratchet cam ring 280 shown in Figures 15(A)-(E) and (G), and the inner peripheral recess 304 and outer peripheral hole 305 of clutch dial 300 shown in Figures 16(A)-(C) and (E) are guide parts that guide the ratchet cam ring 280 and clutch hub 370 to move from the vibration off position to the vibration on position when clutch dial 300 comes to a rotational position corresponding to the vibration mode.

[0147] When clutch dial 300 reaches a rotational position corresponding to the vibration mode, outer peripheral projection 282 of ratchet cam ring 280 faces outer peripheral hole 305 of clutch dial 300, and inner peripheral projection 284 of ratchet cam ring 280 faces inner peripheral recess 304 of clutch dial 300. Then, outer peripheral projection 282 and inner peripheral projection 284 of ratchet cam ring 280 enter the inside of outer peripheral hole 305 and inner peripheral recess 304 of clutch dial 300, respectively, and ratchet cam ring 280 and clutch hub 370 move from the vibration-off position to the vibration-on position due to the bias of ratchet spring 360.

[0148] The inclined portions 286, 287 shown in Figure 15 (G) provided at one circumferential end of the outer peripheral side protrusion 282 and the inner peripheral side protrusion 284 of the ratchet cam ring 280 function to smoothly move the outer peripheral side protrusion 282 and the inner peripheral side protrusion 284, respectively, in and out of the outer peripheral side hole portion 305 and the inner peripheral side recess portion 304 of the clutch dial 300.

[0149] In the vibration-off position, the clutch hub 370 does not restrict the movement of the rear ratchet 410, and in 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.

[0150] Clutch hub 370 is biased forward by ratchet spring 360, and presses forward ratchet cam ring 280. When clutch hub 370 is in the vibration ON position, locking protrusion 373 of clutch hub 370 shown in Figures 18(A) to (D) and locking protrusion 412 of rear ratchet 410 shown in Figures 19(A) to (C), (E) to (F) engage with each other as shown in Figures 22(C) and 26(D).

[0151] As shown in Figures 22(B) and (C), on both circumferential sides of the locking protrusion 373 of the clutch hub 370 and the locking protrusion 412 of the rear ratchet 410, there are provided inclined portions 374, 413 that make it difficult for the clutch hub 370 to move from the vibration-on position to the vibration-off position. Using the angle θ shown in Figures 22(B) and (C), the inclination angle is expressed as θ / 2 in the front-rear direction. When the clutch hub 370 is in the vibration-on position, the inclined portions 374, 413 of the locking protrusions 373, 412 come into contact with each other. When a force in the rotational direction is applied to the rear ratchet 410 in this state, a force in the forward direction is applied to the clutch hub 370 due to the engagement of the inclined portions 374, 413, making it difficult for the clutch hub 370 to move to the vibration-off position.

[0152] 25(A)-(E) and 26(A)-(E) show that, in the process of switching from drill mode to vibration mode, ratchet cam ring 280 and clutch hub 370 move forward due to the bias of ratchet spring 360, and the front-to-rear positions of locking protrusion 373 of clutch hub 370 and locking protrusion 412 of rear ratchet 410 match. In this process, outer circumferential projection 232 and inner circumferential projection 234 of front stopper cam ring 230 move on outer circumferential flat portion 213 and inner circumferential flat portion 215 of rear stopper cam ring 210, and the restriction of rotation of final ring gear 90 by stopper block 120 is effectively maintained.

[0153] When the clutch dial 300 is within a specified rotation range corresponding to the aforementioned clutch mode and drill mode (a rotational position between the states of Figures 23(A)-(E) and the states of Figures 25(A)-(E)), the outer peripheral protrusion 282 and the inner peripheral protrusion 284 of the ratchet cam ring 280 abut against a flat portion (a flat surface perpendicular to the front-to-rear direction) of the clutch dial 300, and the ratchet cam ring 280 and the clutch hub 370 do not move forward (do not move to the vibration on position).

[0154] (How to insert 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 to form the transmission housing. This increases the rigidity of the transmission housing as a whole, and makes it possible to suppress deformation when, for example, the clutch mechanism is activated.

[0155] On the other hand, in a configuration in which the shift arm 71 is extended radially from the rear case 60 through the outside of the screw 44 to the guide hole 64 of the rear case 60, the motor accommodating section 11 that covers the outside of the shift arm 71 becomes larger, leading to an increase in the size of the product.

[0156] As shown in FIGS. 27 to 30, in the work machine 1, the shift arm 71 is passed through the inside of the screw 44 in the radial direction of the rear case 60 and extended to the guide hole 64 of the rear case 60. As shown in FIG.

[0157] When the motor spacer 40, rear case 60, and gear case 140 are fixed by the two upper screws 44, a gap is present between the outer surface of the rear case 60 and the two upper screws 44, and the shift arm 71 extends into this gap.

[0158] The upper two screws 44 have their portions extending in the front-rear direction outside the rear case 60 inserted into a screw collar 45, which is a cylindrical portion separate from the rear case 60. That is, the upper two screws 44 each pass through the screw insertion holes 43 and the screw collar 45 of the motor spacer 40, and are screwed into the screw holes 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 overtightening of the upper two screws 44. The shift arm 71 passes through the gap between the outer circumferential surface of the screw collar 45 and the outer circumferential surface of the rear case 60.

[0159] The two lower screws 44 pass through the screw insertion holes 43 of the motor spacer 40 and the through hole 67 of the rear case 60, and are screwed into the screw holes 151 of the gear case 140. The screw boss portion 62 having the through hole 67 is part of the rear case 60 (integral with the rear case 60), and there is no gap between the screw boss portion 62 and the outer surface of the rear case 60, but this is not a portion through which the shift arm 71 passes, so there is no problem with an increase in size, etc.

[0160] (Sub-handle 600) Fig. 31 to Fig. 39 relate to the sub-handle 600 according to this embodiment. Fig. 31 to Fig. 34 and Fig. 39 show the work machine 1 to which the sub-handle 600 is attached. Fig. 35 to Fig. 38 show the sub-handle 600 alone. The front case 340 is a handle attachment portion of the work machine 1. Note that the sub-handle 600 is not limited to an attachment form extending leftward from the work machine 1 as in Fig. 31 etc., and may also be attached in a form extending rightward from the work machine 1.

[0161] (Opening and closing structure of the mounting part 601) The sub-handle 600 includes a mount portion 601 , a first shaft portion 602 , and a second shaft portion 603 .

[0162] The mount portion 601 is annular with a gap 614 in a portion of the circumferential direction, and engages with the front case 340 of the work 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.

[0163] The first cylindrical portion 612 is provided above the annular portion 615 and on one side (the left side in FIG. 35) of the gap 614 in the length direction of the gap 614 (hereinafter referred to as the "gap length direction"), and extends in the gap length direction.

[0164] The first cylindrical portion 612 has a head holding portion 624 and a shaft insertion portion 626. The head holding portion 624 holds the head 610 of the first shaft portion 602. The head holding portion 624 is located on one side of the shaft insertion portion 626 in the gap length direction (the left side in FIG. 35), and is larger than the shaft insertion portion 626 when viewed from the gap length direction, and is non-circular, for example, hexagonal, into which the head 610 fits. The shaft insertion portion 626 is smaller than the head 610 when viewed from the gap length direction, and the shaft portion 611 of the first shaft portion 602 passes.

[0165] The second cylindrical portion 613 is provided above the annular portion 615 and on one side of the gap 614 in the gap length direction (the right side in FIG. 35), 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 gap length direction.

[0166] The second cylindrical portion 613 has a shaft portion insertion portion 627 and an expanded diameter portion 628. The shaft portion 611 of the first shaft portion 602 passes through the shaft portion insertion portion 627. The expanded diameter portion 628 is located on the other side of the shaft portion insertion portion 627 in the gap length direction (the right side in FIG. 35), has a larger diameter than the shaft portion insertion portion 627, and the shaft portion 611 of the first shaft portion 602 passes through it and an end of the second shaft portion 603 is inserted into it. The pin layer through hole 606 faces the inside of the expanded diameter portion 628. The pin layer through hole 606 opens in a direction intersecting the gap length direction.

[0167] The annular portion 615 has two first anti-rotation recesses 616 and ten second anti-rotation recesses 617 on its inner circumferential 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 portion 601 in between. The ten second anti-rotation recesses 617 are provided at equal angular intervals, five per recess, between the two first anti-rotation recesses 616 in the circumferential direction of the mount portion 601. The first anti-rotation recesses 616 have a longer length in the circumferential direction of the mount portion 601 than the second anti-rotation recesses 617.

[0168] 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.

[0169] 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 in which no external force that widens or narrows the gap 614 is applied to the mount portion 601.

[0170] The first shaft portion 602 extends in the gap length direction, and is provided on the mount portion 601 on one side of the gap 614 in the gap length direction (the left side in FIG. 35) so as to be immovable in the gap length direction. The first shaft portion 602 passes through the gap 614 and protrudes from the mount portion 601 to the other side in the gap length direction.

[0171] The second shaft portion 603 extends in the gap length direction, and is provided on the mount portion 601 on the other side of the gap 614 in the gap length direction (the right side in FIG. 35) so as to be immovable in the longitudinal direction. The second shaft portion 603 protrudes from the mount portion 601 to the other side in the longitudinal direction.

[0172] 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 gap length direction, and the length of the gap 614 can be adjusted by moving the second shaft portion 603 relative to the first shaft portion 602 in the gap length direction.

[0173] The first and second shaft portions 603 are threadedly engaged with each other, and by rotating the second shaft portion 603 with respect to the first shaft portion 602, the second shaft portion 603 can be moved relative to the first shaft portion 602 in the longitudinal direction.

[0174] The first shaft portion 602 has a head portion 610 and a shaft portion 611. The head portion 610 is located on one side of the shaft portion 611 in the gap length direction, and is larger than the shaft portion 611 and has a non-circular shape, for example a hexagonal shape, when viewed from the gap length direction. The head portion 610 fits into the head portion holding portion 624 of the mount portion 601, so that the first shaft portion 602 cannot rotate with respect to the mount portion 601 and the first shaft portion 602 does not slip out of the mount portion 601 to the other side in the gap length direction (the right side in FIG. 35). In addition, a retaining ring 608 provided on the inner peripheral surface of the first cylindrical portion 612 adjacent to the head portion holding portion 624 prevents the first shaft portion 602 from slipping out of the mount portion 601 to one side in the gap length direction (the left side in FIG. 35).

[0175] The shaft portion 611 extends from the head portion 610 to the other side in the gap length direction, passes through shaft portion insertion portions 626, 627 of the mount portion 601, and reaches the inside of the second shaft portion 603. A male thread portion 622 is provided on the outer circumferential surface of the tip portion of the shaft portion 611.

[0176] The second shaft portion 603 has, in order from the other side in the gap length direction, a grip portion 604, a large diameter portion 618, and a small diameter portion 619.

[0177] The small diameter portion 619 is inserted into the expanded diameter portion 628 of the second cylindrical portion 613 of the mounting portion 601. Both the small diameter portion 619 and the expanded 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 each grooves that 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.

[0178] 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 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 into the pin insertion groove 620, making the second shaft portion 603 immovable in the gap length direction relative to the second cylindrical portion 613 of the mount portion 601.

[0179] The second shaft portion 603 is rotatable relative to the second cylindrical portion 613. An 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 portion 603 relative to the second cylindrical portion 613, and prevents the second shaft portion 603 from easily rotating.

[0180] The second shaft portion 603 has a nut portion 623 that constitutes a female thread portion. The nut portion 623 screws into the male thread 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 with them. In the example of Fig. 35, the nut portion 623 is a separate part from the large diameter portion 618 and the small diameter portion 619.

[0181] When the grip portion 604 is turned, the entire second shaft portion 603 rotates integrally with respect to the mount portion 601 and the first shaft portion 602. In conjunction with this, the second shaft portion 603 moves in the gap length direction relative to the first shaft portion 602 due to threaded engagement between the male thread portion 622 of the first shaft portion 602 and the nut 623 of the second shaft portion 603. At this time, the second shaft portion 603 moves in the gap length direction relative to the first cylindrical portion 612 due to engagement between the second shaft portion 603 and the second cylindrical portion 613 of the mount portion 601 via the pin 607. This adjusts the length of the gap 614.

[0182] 38(B) and (E), that is, when the gap 614 is at its natural length, by turning the grip portion 604 to the left, the second shaft portion 603 is relatively moved to the other side in the gap length direction (the right side in FIG. 38), and the length of the gap 614 can be adjusted to be longer than the natural length. FIGS. 38(C) and (F) show the state in which the length of the gap 614 is at its maximum, that is, the state in which the mount portion 601 is fully opened. The length of the threaded engagement between the male thread portion 622 of the first shaft portion 602 and the nut 623 of the second shaft portion 603 is set so that the upper limit of the length of the gap 614 is within a predetermined length at which the mount portion 601 is not damaged.

[0183] 38(B) and (E), that is, when the gap 614 is at its natural length, by turning the grip portion 604 to the right, the second shaft portion 603 and the second cylindrical portion 613 of the mount portion 601 are moved relatively to one side in the gap length direction (the left side in FIG. 35), and the length of the gap 614 can be adjusted to be shorter than the natural length. FIGS. 38(A) and (D) show the state in which the length of the gap 614 is at its minimum, that is, the state in which the mount portion 601 is most closed. By adjusting the length of the gap 614 to be shorter than the natural length, the mount portion 601 can be tightened to the front case 340, and the sub-handle 600 can be fixed to the front case 340.

[0184] By opening the gap 614 wider than its natural length, the front case 340 of the work machine 1 can be passed inside the mount part 601. The anti-slip protrusion 350 of the front case 340 has a large dimension such that the mount part 601 cannot be inserted inside the mount part 601 when the gap 614 is at its natural length. The anti-slip protrusion 350 inhibits (prevents) the mount part 601 from slipping forward from the front case 340 when the gap 614 is at or below its natural length.

[0185] (Easy-to-store structure of the sub-handle 600) To attach the sub-handle 600 to the front case 340, the length of the gap 614 is adjusted to be longer than the natural length, and the mount part 601 is fitted into the front case 340 from the front. After that, the grip part 604 is turned to the right to reduce the gap 614.

[0186] When attaching the sub-handle 600 to the front case 340, the attachment angle can be selected from a number of stages. Of the two first anti-rotation recesses 616 and ten second anti-rotation recesses 617 of the mount part 601, two that correspond to the attachment angle of the sub-handle 600 relative to the front case 340 engage with the two anti-rotation protrusions 349 of the front case 340 in a concave-convex manner.

[0187] 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.

[0188] When the second anti-rotation recess 617 of the mount part 601 and the anti-rotation protrusion 349 of the front case 340 are engaged with each other, the circumferential lengths of both are approximately equal, so that the sub-handle 600 can be attached to the front case 340 without rattling or with minimal rattling. The second anti-rotation recess 617 of the mount part 601 is used when the sub-handle 600 is not stored, i.e., when the work machine 1 is in use.

[0189] When the first anti-rotation recess 616 of the mount part 601 and the anti-rotation protrusion 349 of the front case 340 engage with each other, the circumferential length of the first anti-rotation recess 616 is longer than the circumferential length of the anti-rotation protrusion 349, so that the sub-handle 600 can rotate within a predetermined angle range relative to the front case 340. The first anti-rotation recess 616 is used when the sub-handle 600 is stored, i.e., when the work machine 1 is not in use.

[0190] 39(A) to (C) are diagrams showing that the sub-handle 600 can be rotated within a predetermined angle range in the stored state.

[0191] Fig. 39(A) shows a state in which the sub-handle 600 has been rotated to the maximum extent in the counterclockwise direction in the drawing. This state is a first engagement state in which the circumferential end portions of the first anti-rotation recess 616 of the mount part 601 and the anti-rotation protrusion 349 of the front case 340 engage with each other, as shown enlarged in Fig. 39(B).

[0192] 39(B) shows a state in which the sub-handle 600 is in the center of the rotatable range. This state is a second engagement state in which the circumferential ends of the first anti-rotation recess 616 of the mount portion 601 and the one circumferential end of the anti-rotation protrusion 349 of the front case 340 do not come into contact with each other. Note that in the second engagement state, the first anti-rotation recess 616 of the mount portion 601 and the other circumferential end of the anti-rotation protrusion 349 of the front case 340 may engage with each other.

[0193] Even when the first anti-rotation recess 616 of the mounting portion 601 and the anti-rotation protrusion 349 of the front case 340 are engaged with each other, by making the gap 614 of the mounting portion 601 equal to or shorter than a predetermined length that is shorter than the natural length, the frictional force caused by the mounting portion 601 tightening against the front case 340 prevents the sub-handle 600 from rotating relative to the front case 340.

[0194] This embodiment provides the following advantages.

[0195] (1) The work machine 1 includes an output switching unit 6 that switches the output (torque or the presence or absence of vibration) of the output unit 7, the output switching unit 6 being disposed between the output unit 7 and the transmission unit 5. When the transmission unit 5 is removed from the output unit 7, the output switching unit 6 can be removed rearward from the output unit 7. Specifically, when the screw 133 is removed and the gear case 140 is removed from the front case 340 (the transmission unit 5 is removed from the output unit 7), the output switching unit 6 can be removed rearward from the output unit 7. Therefore, even if the fixation of the spindle 470 and the chuck 500 cannot be released, the components of the output switching unit 6, i.e., the clutch dial 300, the nut 260, the clutch spring 250, and other components, can be replaced, and repairability is good.

[0196] For comparison, a configuration in which the gear case 140 is extended forward, ball bearings 335 and 461 are held, and a retaining ring is used to prevent the clutch dial 300 from slipping out of the gear case 140 forward (hereinafter, "Comparative Configuration 1") will be considered. 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 forward or backward. Therefore, in Comparative Configuration 1, when the clutch dial 300 and the like are damaged and need to be replaced, it is necessary to take measures such as removing the chuck 500 from the spindle 470 using a special tool or replacing the entire transmission / output component 4, which increases the time or cost required for repair. This embodiment is intended to suitably solve such problems.

[0197] (2) The transmission unit 5 and the output unit 7 are modular and can be commonly used in multiple models, which is highly convenient.

[0198] (3) The work machine 1 includes the transmission mechanism 50 including the final ring gear 90, the stopper block 120 that disables the rotation of the final ring gear 90 when the work machine 1 is in the locked position, and the stopper spring 117 that biases the stopper block 120 toward the locked position. Therefore, even if the front end of the convex portion 123 of the stopper block 120 that is moving to the locked position comes into contact with the rear end of the outer circumferential convex portion 91 of the final ring gear 90 and the stopper block 120 cannot reach the locked position, if the final ring gear 90 subsequently rotates, the outer circumferential convex portion 91 moves from the front of the convex portion 123, and the stopper block 120 automatically moves to the locked position. This makes it possible to suppress a malfunction that makes it impossible to disable the rotation of the final ring gear 90, that is, a malfunction that makes it impossible to switch to the drill mode.

[0199] (4) In the work machine 1, the position of the stopper block 120 can be switched between the locked position and the unlocked position by the clutch dial 300. Specifically, when the clutch dial 300 is rotated to the rotation position for the drill mode, the stopper block 120 moves to the locked position. Here, the force that moves the stopper block 120 to the locked position is the biasing force of the stopper spring 117, and is not due to thread 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 possible to suppress a malfunction in which the clutch dial 300 cannot be rotated to the rotation position for the drill mode, and this is easy to use.

[0200] (5) Stopper spring 117 is configured to bias stopper block 120 forward, and stopper spring 117 and stopper block 120 are provided rearward of clutch dial 300. Therefore, compared to the case where stopper spring 117 and stopper block 120 are provided inside clutch dial 300, the diameter of clutch dial 300 can be prevented from becoming larger, and deterioration in operability when rotating clutch dial 300 can be prevented.

[0201] (6) When the clutch dial 300 is within the rotation range of the clutch mode, the rear stopper cam ring 210 and the front stopper cam ring 230 function as a regulating portion that regulates the movement of the stopper block 120 from the non-locking position to the locking position against the biasing force of the stopper spring 117. In addition, the rear stopper cam ring 210 and the front stopper cam ring 230 form 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 between the rotation position of the drill mode and the rotation position of the clutch mode. Therefore, the forward and backward movement of the stopper block 120 is limited to when the clutch dial 300 rotates between the rotation position of the drill mode and the rotation position of the clutch mode, and the forward and backward movement of the stopper block 120 (movement between the non-locking position and the locking position) can be suitably realized without relying on the threaded engagement between the clutch dial 300 and the nut 260.

[0202] (7) When the clutch dial 300 rotates between the rotation position for the drill mode and the rotation position for the clutch mode, the outer peripheral protrusion 232 and the inner peripheral protrusion 234 of the front stopper cam ring 230 move along the outer peripheral inclined portion 212 and the inner peripheral inclined portion 214 of the rear stopper cam ring 210. Here, by making the inclination angle of the outer peripheral inclined portion 212 and the inner peripheral inclined portion 214 steeper than the inclination of the threaded portion 301 of the clutch dial 300, the stopper block 120 can be moved significantly forward and backward in conjunction with the rotation of the clutch dial 300, compared to the case where the stopper block 120 is moved by the threaded engagement between the clutch dial 300 and the nut 260. This reduces the amount of operation of the clutch dial 300 required to switch between the clutch mode and the drill mode, making it easy to use. In addition, since the outer circumferential inclined portion 212 and the inner circumferential inclined portion 214 form a recess, the outer circumferential protrusion 232 and the inner circumferential protrusion 234 of the front stopper cam ring 230 can easily enter and exit the recess. This reduces the risk of jamming when switching between the clutch mode and the drill mode, improving usability.

[0203] (8) The rear stopper cam ring 210 is located forward of the final ring gear 90, and the stopper block 120 protrudes forward of the final ring gear 90 to engage 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 and disposed in front of and behind the final ring gear 90. Therefore, unlike a case in which the configuration for switching to the drill mode is biasedly disposed either in front of or behind the final ring gear 90, it is easy to balance the radial sizes of the gear case 140 and the clutch dial 300, and layout efficiency is good.

[0204] (9) When the clutch hub 370 of the work machine 1 reaches the vibration-on position, the clutch hub 370 restricts the movement of the rear ratchet 410. The front ratchet 440 is driven by the driving force of the motor 30 with respect to the restricted movement of the rear ratchet 410, generating vibration. When the clutch dial 300 reaches a rotational position corresponding to the vibration mode, the outer peripheral projection 282 and the inner peripheral projection 284 of the ratchet cam ring 280 enter the inside of the outer peripheral hole 305 and the inner peripheral recess 304 of the clutch dial 300 along their own inclined portions 286 and 287, respectively, and the ratchet cam ring 280 and the clutch hub 370 move from the vibration-off position to the vibration-on position due to the bias of the ratchet spring 360. Therefore, compared to a configuration in which the clutch hub 370 is pushed forward by the 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 on and off of vibration can be reduced, making it easier to use.

[0205] (10) Since outer circumferential projection 282 and inner circumferential projection 284 of ratchet cam ring 280 have inclined portions 286, 287, outer circumferential projection 282 and inner circumferential projection 284 can smoothly move in and out of outer circumferential hole 305 and inner circumferential recess 304 of clutch dial 300, thereby reducing snagging when switching between drill mode and vibration mode, and improving usability.

[0206] (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 function as a restricting portion that restricts the movement of the clutch hub 370 from the vibration off position to the vibration on position against the biasing force of the ratchet spring 360. In addition, the ratchet cam ring 280 and the clutch dial 300 constitute a cam mechanism that moves 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 rotation position of the vibration mode and the rotation position of the drill mode. Therefore, the forward and backward movement of the clutch hub 370 is limited to when the clutch dial 300 rotates between the rotation position of the vibration mode and the rotation position of the drill mode, and the forward and backward movement of the clutch hub 370 (movement between the vibration off position and the vibration on position) can be suitably realized without relying on the threaded engagement between the clutch dial 300 and the nut 260.

[0207] (12) As shown in Figures 22(B) and (C), on both circumferential sides of the locking protrusion 373 of the clutch hub 370 and the locking protrusion 412 of the rear ratchet 410, inclined portions 374, 413 are provided to make it difficult for the clutch hub 370 to move from the vibration ON position to the vibration OFF position. When a force in the rotational direction is applied to the rear ratchet 410 in the vibration ON position, a force in the forward direction is applied to the clutch hub 370 due to the engagement between the inclined portions 374, 413, making it difficult for the clutch hub 370 to move to the vibration OFF position. This prevents the clutch hub 370 from moving inadvertently to the vibration OFF position due to vibration or the like.

[0208] (13) The motor spacer 40, the rear case 60, and the gear case 140 are fixed with four screws 44 to form a transmission housing with high rigidity, which can suppress deformation when the clutch mechanism is activated. Meanwhile, 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 through the outside of the screws 44 in the radial direction of the rear case 60 to the guide hole 64 of the rear case 60, it is possible to suppress an increase in size of the motor accommodating portion 11 that covers the outer side of the shift arm 71, and thus suppress an increase in size of the product.

[0209] (14) The two upper screws 44 have their portions extending in the front-rear direction on the outside of the rear case 60 inserted into the screw collar 45, which is a cylindrical portion separate from the rear case 60. This prevents the motor spacer 40 from being bent or damaged due to overtightening of the two upper screws 44.

[0210] (15) The front case 340 has the protrusions 350 for preventing the sub-handle 600 from falling off, which prevents the sub-handle 600 from falling off forward due to vibrations or the like during work, improving workability.

[0211] (16) The sub-handle 600 is annular with a gap 614 in a portion of its circumference, and includes a mount portion 601 that engages with the front case 340 of the work machine 1, and is configured so that the length of the gap 614 can be adjusted within a predetermined range including a length longer than the natural length. Therefore, even if the length of the gap 614 in the front case 340 in its natural length interferes with, for example, the retaining protrusion 350 of the front case 340, making attachment and detachment difficult, the length of the gap 614 can be adjusted to be longer than the natural length to make it easily attachable and detachable.

[0212] (17) First shaft portion 602 and second shaft portion 603 are threadedly engaged with each other, and the length of gap 614 can be adjusted by turning grip portion 604 provided on second shaft portion 603. Therefore, the length of gap 614 can be easily adjusted, making it easy to use.

[0213] (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 gap length direction relative to the second cylindrical portion 613 of the mount portion 601. Since the pin 607 allows the second shaft portion 603 to rotate, the length of the gap 614 can be adjusted by turning the second shaft portion 603.

[0214] (19) The O-ring 609 generates frictional resistance against the rotation of the second shaft portion 603 relative to the second cylindrical portion 613, which prevents the second shaft portion 603 from rotating easily, improving workability.

[0215] (20) The length of threaded engagement between male thread portion 622 of first shaft portion 602 and nut 623 of second shaft portion 603 is set so that the upper limit of the length of gap 614 is within a predetermined length that does not damage mount portion 601. Therefore, regardless of the degree of operation by the user, damage to mount portion 601 caused by excessive widening of gap 614 can be suppressed, and usability is good.

[0216] (21) The mount portion 601 has a first anti-rotation recess 616 having a long circumferential length and a second anti-rotation 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 in a concave-convex manner, the circumferential lengths of the two are approximately equal, so that the sub-handle 600 can be attached to the front case 340 without rattling or with minimal rattling, enabling 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 in a concave-convex manner, the circumferential length of the first anti-rotation recess 616 is longer than the circumferential length of the anti-rotation protrusion 349, so that the sub-handle 600 can be rotated within a predetermined angle range relative to the work machine 1 in the stored state as shown in Figures 39(A) and (C), that is, the attached state can be finely adjusted. Therefore, the workability of storing the sub-handle 600 in the work machine 1 is good. If the angle when stored cannot be changed from the angle shown in Figure 39 (C), the flange portion 625 of the grip portion 604 will interfere with the battery pack 25, the battery pack attachment portion 13, etc., making it difficult to store the battery pack, but this embodiment can advantageously solve such problems.

[0217] (22) Even when the first anti-rotation recess 616 of the mount portion 601 and the anti-rotation protrusion 349 of the front case 340 engage with each other in a concave-convex manner, by setting the gap 614 of the mount portion 601 to a predetermined length or less that is shorter than the natural length, the sub-handle 600 can be made unrotatable relative to the front case 340 by the frictional force caused by the mount portion 601 tightening the front case 340. This makes it possible to suppress rattling of the sub-handle 600 in the stored state as necessary. Also, even when the first anti-rotation recess 616 of the mount portion 601 is configured to be used when the work machine 1 is in use, rattling during work can be suppressed.

[0218] Although the present invention has been described above by taking the embodiment as an example, the present invention is not limited to the embodiment. Various modifications can be made to each of the details specifically described in the embodiment within the scope of the claims.

[0219] The concave-convex structure exemplified in the embodiment may have a concave-convex relationship 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.

[0220] The number of outer peripheral convex portions 91 of the final ring gear 90 and the number of stopper blocks 120, the number of screws 44, 133, the number of stages of set tightening torque, the number of possible attachment angles of the sub-handle 600 to the work machine 1, the number of first anti-rotation recesses 616 and second anti-rotation recesses 617, etc., which are given as specific numbers in the embodiment, do not limit the scope of the invention in any way and can be changed as desired to suit the required specifications. [Explanation of symbols]

[0221] 1...work machine, 4...transmission / output component, 5...transmission section, 6...output switching section, 7...output section, 10...housing, 11...motor accommodating section, 12...handle section, 13...battery pack mounting section, 15...tail cover, 17...trigger switch, 19...forward / reverse switching 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 section, 42...gear section, 43...screw insertion hole, 45...screw collar, 50...transmission mechanism (reduction mechanism), 51...first planetary gear, 53...needle bearing, 55...first carrier, 57...slide ring gear, 58...groove portion, 60...rear case, 61...cylindrical portion, 62...screw boss portion, 63...guide protrusion portion, 64...guide hole, 65...spring retaining hole, 66...flange portion, 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 circumferential protrusion portion, 92...cylindrical portion, 93...flange portion, 94...gear portion, 95...front protrusion portion, 96 ...front recess, 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 retaining portion, 123...locking protrusion (projection), 124...wide protrusion, 131...clutch pin, 133...screw, 135...spring washer, 140...gear case, 141...rear cylindrical portion, 142...front wall portion, 143...through hole, 144...rotation stop portion, 145...through hole, 146...central through hole, 147...through hole, 148... Anti-rotation portion protrusion, 149...anti-rotation portion protrusion, 150...front cylindrical portion, 151...screw hole, 152...stopper insertion groove, stopper insertion hole, 161...pin sleeve, 165...thrust plate, 210...rear stopper cam ring, 211...flat portion, 212...outer peripheral side inclined portion, 213...outer peripheral side flat portion, 214...inner peripheral side inclined portion, 215...inner peripheral side flat portion, 218...anti-rotation recess, 219...anti-rotation recess, 230...front stopper cam ring, 232...outer peripheral side projection, 234...inner peripheral side projection, 235...locking projection, 250...clutch spring, 260...nut, 261...threaded portion,262...spring locking hole, 263...notch, 280...ratchet cam ring, 282...outer circumferential projection, 284...inner circumferential projection, 285...rotation stopper protrusion, 286...inclined portion, 287...inclined portion, 288...small protrusion, 300...clutch dial, 301...threaded portion, 302...locking recess, 304...inner circumferential recess, 305...outer circumferential hole, 306...tubular portion, 307...front wall, 308...leaf spring mounting portion, 331...leaf spring, 335...ball bearing, 340...front case, 34 1...large diameter cylindrical portion, 342...small diameter cylindrical portion, 343...connection surface portion, 344...notch portion, 345...screw boss portion, 346...screw hole, 347...screw hole, 348...bearing retaining portion, 349...rotation prevention protrusion portion (rotation regulating portion), 350...removal prevention protrusion portion, 351...locking recess portion, 360...ratchet spring, 370...clutch hub, 371...annular portion, 372...outer protrusion portion, 373...locking protrusion portion, 374...inclined portion, 391...thrust bearing, 395...bearing washer, 410...rear ratchet, 411...uneven portion (vibration generating shape portion), 412...engagement protrusion, 413...inclined portion, 431...spring, 435...ratchet washer, 440...front ratchet, 441...uneven portion (vibration generating shape portion), 461...ball bearing, 470...spindle, 481...O-ring, 483...retaining ring, 485...bearing cover, 487...through hole, 489...screw, 495...left-handed screw, 500...chuck, 600...sub-handle, 601...mounting portion, 602...first shaft portion, 603...second shaft portion, 604...grip portion, 6 05...knob bolt, 606...pin layer through hole, 607...pin, 608...retaining ring, 609...O-ring, 610...head, 611...shaft, 612...first cylindrical portion, 613...second cylindrical portion, 614...gap, 615...annular portion, 616...first anti-rotation recess, 617...second anti-rotation recess, 618...large diameter portion, 619...small diameter portion, 620...pin insertion groove, 621...O-ring insertion groove, 622...male thread portion, 623...nut portion, 624...head holding portion, 625...flange portion, 626...shaft insertion portion, 627...shaft insertion portion, 628...expanded diameter portion.

Claims

1. A motor; a reduction mechanism having a ring gear and reducing the rotation speed of the motor; a stopper portion that is movable between a locking position and an unlocking position and prevents the ring gear from rotating when the stopper portion is in the locking position; and a biasing means for biasing the stopper portion toward the locking position. A work machine characterized by:

2. A clutch dial that is operated by an operator to adjust the set tightening torque; a clutch mechanism that stops rotation of the ring gear until the set tightening torque is reached, but allows rotation of the ring gear when the tightening torque reaches or exceeds the set tightening torque; A work machine capable of selecting at least one of a clutch mode in which the clutch mechanism cuts off the transmission of rotation from the transmission mechanism to the spindle when the set tightening torque is exceeded, and a drill mode in which the ring gear is made unrotatable without using the clutch mechanism, a switching operation unit configured as the clutch dial and capable of switching a position of the stopper unit between the locking position and the non-locking position, When the clutch mode is selected, the stopper portion is in the non-engaging position, and the stopper portion does not engage with the ring gear in the rotational direction, When the switching operation unit is operated to a predetermined position corresponding to the drill mode from a state in which the clutch mode is selected, the stopper portion is moved from the non-engagement position to the engagement position by the urging means, and the stopper portion is engaged with the ring gear in the rotational direction, thereby switching to the drill mode.

2. The work machine according to claim 1 .

3. The switching operation unit is located on one side of the ring gear in the axial direction of the motor, The biasing means biases the stopper portion toward one side in the axial direction.

3. The work machine according to claim 2.

4. an end portion of the stopper portion on one side in the axial direction protrudes toward the one side in the axial direction beyond the ring gear; 4. The work machine according to claim 3.

5. a restricting portion that restricts movement of the stopper portion from the unlocked position to the locked position against the bias of the biasing means, The restriction by the restricting unit can be switched between restriction and release by operating the switching operation unit.

4. The work machine according to claim 3.

6. the switching operation unit is a dial that is rotatable around an extension of an axis of the motor, The regulating portion includes a cam mechanism that moves the stopper portion between the unlocked position and the locked position in response to rotation of the dial.

6. A work machine according to claim 5.

7. The regulating portion is a first cam that is located on one side of the stopper portion in the axial direction, contacts the stopper portion, and is biased by the biasing means toward the one side in the axial direction via the stopper portion, so that rotation of the first cam is restricted; a second cam located on one side of the first cam in the axial direction and rotating together with the dial, When the second cam reaches a predetermined rotation position, the first cam moves to one side in the axial direction, and the restriction by the restricting portion is released.

7. A work machine according to claim 6.

8. one of the first and second cams has a recess or a hole and the other has a protrusion, When the second cam reaches the predetermined rotation position, the convex portion enters the concave portion or the hole portion, the first cam moves to one side in the axial direction, and the restriction by the restricting portion is released. A work machine according to claim 7.

9. At least one of the first and second cams has an inclined portion that makes it easy for the protrusion to enter and exit the recess or hole. A work machine according to claim 8.

10. the first cam contacts the stopper portion on an outer side of the ring gear in a radial direction of the ring gear; 9. A work machine according to claim 7 or 8.

11. The first cam is located on one side of the ring gear in the axial direction.

9. A work machine according to claim 7 or 8.

12. A tool holder; a clutch mechanism that interrupts transmission of rotation from the reduction mechanism to the tool holder at a predetermined torque, the dial is capable of switching the predetermined torque within a predetermined rotation range, When the dial is within the predetermined rotation range, the second cam does not come to the predetermined rotation position.

9. A work machine according to claim 7 or 8.

13. the stopper portion has a protrusion portion that is located radially inward of a contact portion with the first cam and that engages with the ring gear when the stopper portion is in the locking position; A work machine according to claim 10.

14. A motor, a reduction mechanism having a planetary gear mechanism including a planetary gear and a ring gear, the reduction mechanism reducing the rotation speed of the motor; a spindle that is rotationally driven by the motor via the reduction mechanism and rotates together with a chuck that holds a tool bit; A clutch dial that is operated by an operator to adjust the set tightening torque; a clutch mechanism that stops rotation of the ring gear until the set tightening torque is reached, but allows rotation of the ring gear when the tightening torque reaches or exceeds the set tightening torque; A work machine capable of selecting at least one of a clutch mode in which the clutch mechanism cuts off the transmission of rotation from the transmission mechanism to the spindle when the set tightening torque is exceeded, and a drill mode in which the ring gear is made unrotatable without using the clutch mechanism, a stopper portion that is movable between a locking position and an unlocking position, and that, when in the locking position, engages with the ring gear in a rotational direction to prevent the ring gear from rotating, and, when in the unlocking position, does not engage with the ring gear in the rotational direction to allow the ring gear to rotate; a switching operation unit that can switch a position of the stopper unit between the locking position and the unlocking position by an operation of an operator; a biasing means for biasing the stopper portion toward the locking position; a restricting portion capable of restricting movement of the stopper portion from the non-locking position to the locking position against the bias of the biasing means, the restricting portion switching between restricting the movement of the stopper portion from the non-locking position to the locking position and releasing the restriction of the movement of the stopper portion from the non-locking position to the locking position by operating the switching operation portion, When the switching operation unit is operated to a predetermined position corresponding to the drill mode from a state in which the clutch mode is selected, the restriction of the movement of the stopper unit from the non-engaging position to the engaging position by the restricting unit is released, the stopper unit moves from the non-engaging position to the engaging position by the biasing means, and the stopper unit engages with the ring gear in the rotational direction, thereby switching to the drill mode. A work machine characterized by:

15. The switching operation unit is configured as the clutch dial, A work machine according to claim 14.

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