Work equipment

Abstract

To provide a work machine that can reduce time and effort required in switching between presence and absence of vibrations.SOLUTION: In a work machine 1, when a clutch hub 370 comes to a vibration-on position, the clutch hub 370 restricts movement of a rear-side ratchet 410. When a front-side ratchet 440 is driven by driving force of a motor 30 with respect to the rear-side ratchet 410 with movement restricted, vibrations occur. A ratchet cam ring 280 and a clutch dial 300 constitute a cam mechanism that moves the clutch hub 370 between a vibration-off position and a vibration-on position in tandem with rotation of the clutch dial 300 between a rotating position in a vibration mode and a rotating position in a drill 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, and 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 interrupts the transmission of rotation from the transmission mechanism to the spindle at a predetermined torque.

[0004] The reduction ratio switching mechanism has a shift knob operated by the 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 specified torque. Driver drills with a vibration function, such as those described in Patent Document 2, are also called vibration driver drills, and the vibration can be turned on or off by operating the clutch dial. [Prior art documents] [Patent documents]

[0005] [Patent Document 1] Japanese Patent Application Laid-Open No. 2014-018914 [Patent Document 2] Japanese Patent Application Laid-Open No. 2015-191735 [Patent Document 3] Japanese Patent Application Laid-Open No. 2017-80853 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 high torque, and a special jig is required to release the fixation. In other words, without the special jig, the chuck and spindle essentially become a single tool holder. This makes it difficult to replace parts that cannot be removed without releasing the fixation between the chuck and spindle. Conventional work machines have many parts that are difficult to replace, making them difficult to repair. The first problem recognized by the inventor is to provide a work machine that is easy to repair.

[0007] A work machine such as a driver drill can enter drill mode, which maximizes torque, by immobilizing the ring gear of the transmission mechanism. One configuration for entering drill mode involves pushing a stopper pin toward the ring gear using a nut that rotates with the clutch dial and moves axially. Depending on the rotational position of the ring gear, a portion of the ring gear may be located on the extension of the stopper pin. With this configuration, if the stopper pin hits this portion, the clutch dial cannot be turned, preventing the machine from switching to drill mode, resulting in poor usability. The second problem recognized by the inventors is to provide a work machine that can prevent problems that prevent the ring gear from being immobilized.

[0008] In a work machine such as a driver drill, when the 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 cases and suppress deformation. However, if the shift arm passes outside the fixing parts in the radial direction of the case, the product will become larger in the radial direction. The third problem recognized by the inventors is to provide a work machine that can suppress the increase in size.

[0009] In a work machine such as a vibration driver drill, if the clutch dial operation required to switch between vibration on and off is large, switching between vibration on and off takes time and effort, resulting in poor workability. The fourth problem recognized by the present inventors is to provide a work machine that can reduce the time required to switch between vibration on and off.

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

[0011] If the handle cannot be moved while attached to the work machine, it is not possible to fine-tune the attachment state of the handle, which can be inconvenient. A sixth problem recognized by the present inventors is to provide a handle whose attachment state to the work machine can be fine-tuned, and a work machine equipped with a handle whose attachment state can be fine-tuned.

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

[0013] One aspect of the present invention is a work machine. A motor; a tool holder driven by the motor; a vibration unit that outputs the driving force of the motor to the tool bit holder as vibration; a switching operation unit that switches between a vibration-on state and a vibration-off state of the vibration unit; a vibration switching unit that moves from a vibration off position to a vibration on position in response to an operation of the switching operation unit, A guide unit is provided to guide the vibration switching unit to move from the vibration-off position to the vibration-on position when the switching operation unit reaches a predetermined position. death , the guide portion includes a recess or a hole provided in one of the switching operation portion and the vibration switching portion and a protrusion provided in the other of the switching operation portion and the vibration switching portion, a biasing portion that biases the vibration switching portion in a direction in which the convex portion enters the concave portion or the hole portion, When the switching operation unit reaches a predetermined position, the recess or hole and the protrusion face each other, and the protrusion enters the recess or hole, and the vibration switching unit moves from the vibration-off position to the vibration-on position due to the biasing force of the biasing unit. It is characterized by do.

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

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

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

[0017] This embodiment relates to a work machine 1. The work machine 1 is a vibration driver drill. Figures 3 and 4 define the front-rear and up-down directions of the work machine 1, which are perpendicular to each other. Furthermore, the left-right directions, which are perpendicular to the front-rear and up-down directions, are defined based on a worker facing forward.

[0018] The front-to-rear direction is a direction parallel to the axial direction of the motor shaft 31. The front side corresponds to one side of the axial direction. The rear side corresponds to the other side of the axial direction. The up-down direction is a direction connecting the motor accommodating section 11 and the battery pack mounting section 13 perpendicular to the front-to-rear direction.

[0019] As shown in Figures 1 to 4, the work machine 1 includes a housing 10. The housing 10 is, for example, a resin molded body having a structure in which it is divided into two parts, left and right. The housing 10 includes a motor housing portion 11, a handle portion 12, and a battery pack mounting portion 13.

[0020] The motor housing 11 is a cylindrical portion whose central axis is parallel to the front-to-rear direction. The work machine 1 is provided with a tail cover 15 that covers the rear opening of the motor housing 11. The work machine 1 is provided with a shift knob 21 on top of the motor housing 11. The shift knob 21 is a reduction ratio switching operation unit that rotates a shift arm 71 that appears in Figures 5 to 7 to move a slide ring gear 57 (described below) back and forth, thereby switching the reduction ratio of the transmission mechanism 50 shown in Figure 5. The shift arm 71 is made of, for example, metal, and corresponds to the reduction ratio switching unit.

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

[0022] The battery pack attachment section 13 is connected to the lower end of the handle section 12. A battery pack 25, which 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 (the 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 other components. 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 corresponding to the rotational position of the motor 30.

[0024] (Configuration of transmission and 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 cover 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. In other words, 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 first fixing parts, and the lower two screws 44 correspond to second fixing parts. The screws 44 extend in the front-to-rear direction. The screw collar 45 that appears in Figures 6 and 7 is made of, for example, metal, and is a member through which the upper two screws 44 pass.

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

[0030] As shown in Figures 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 holding hole 65, a flange portion 66, and two through holes 67.

[0031] The cylindrical 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 cylindrical portion 61 so as to protrude radially outward. The through-holes 67 pass through the screw boss portions 62 in the front-rear direction. The through-holes 67 are portions 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 movement of the lower part of the shift arm 71 in the front-rear direction. The spring holding hole 65 is a blind hole that opens to the front surface of the flange 66 and holds the rear end of the stopper spring 117 that appears in Figures 5 to 7. The flange 66 extends radially outward 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 and 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 leaking 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 Figures 9(A) to (G), the final ring gear 90 has six outer peripheral convex portions 91 (protrusions), 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 of the cylindrical portion 92. The six outer peripheral convex portions 91 are arranged at equal angular intervals in the circumferential direction, and each protrudes radially outward from the front portion of the outer peripheral surface of the cylindrical portion 92. The outer peripheral convex portions 91 are provided across 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. The rear end portion of the clutch pin 131, which will be described later, is pressed against the front concave portion 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 10(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-like 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 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 peripheral surface of the final ring gear 90. The locking protrusion 123 is a protrusion that engages with an outer peripheral 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 wider circumferential width than 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), the 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 and 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 part of the outer shell of the work machine 1. The front wall portion 142 connects the front portion of the rear cylindrical portion 141 and the 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 and 7.

[0046] The three anti-rotation portions 144 are arranged at equal angular intervals in the circumferential direction, and each protrudes forward as a fork from the front end of the front cylindrical portion 150. The anti-rotation portions 144 sandwich anti-rotation protrusions 285 of the ratchet cam ring 280 (described later) from both sides in the circumferential direction, 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 are passed, and correspond to the transmission unit housing-side mounting portions. The spring washers 135 appearing in FIGS. 6 to 7 are made of, for example, metal, 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 is passed. The four through holes 147 are portions through which the screws 27 appearing in FIG. 1 are passed, i.e., the screws 27 used to fix the gear case 140 to the motor accommodating portion 11 from the front.

[0048] Anti-rotation protrusions 148, 149 are protrusions that engage (fit) with anti-rotation recesses 218, 219 of rear stopper cam ring 210, which will be described later, 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, which appear in Figures 6 and 7, are threaded.

[0049] The three stopper insertion grooves 152 are recessed grooves that are provided at equal angular intervals in the circumferential direction on the inner peripheral 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 stopper insertion groove 152. The stopper block 120 is guided by the stopper insertion grooves 152 and can 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 joined together by four screws 44 to form a transmission housing that houses 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 that make up 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 peripheral 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 as the shift arm 71 rotates.

[0055] When the slide ring gear 57 is positioned forward, it meshes with the second planetary gear 81. At this time, the slide ring gear 57 is fixed so as not to be rotatable 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 periphery of the final carrier 101 and the outer periphery of the rear end of the spindle 470, transmitting the rotation of the final carrier 101 to the spindle 470. The final carrier 101 is made of, for example, metal.

[0058] The rollers 103 and lock ring 110 shown in Figures 6 and 7 are made of metal, for example, and are components that suppress 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 rollers 103 are sandwiched and fixed between the outer periphery of the spline hub 105 and the inner periphery of the lock ring 110. The components are positioned such that the rollers 103 are not fixed when rotation is transmitted from the final carrier 101 side to the spindle 470 and chuck 500 side.

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

[0060] The transmission / output component 4 includes a rear stopper cam ring 210 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 Figures 12(A) to (G), rear stopper cam ring 210 has 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 flat portion perpendicular to the front-to-rear direction and provided on the front surface of the rear stopper cam ring 210. The outer peripheral inclined portion 212 is provided on the radially outer portion of the front surface of the rear stopper cam ring 210. One end of the outer peripheral inclined portion 212 is connected to the flat portion 211, and is an inclined surface that inclines from the flat portion 211 so that it becomes more rearward as it moves clockwise in a front view. The outer peripheral flat portion 213 is a flat portion perpendicular to the front-to-rear direction and extends circumferentially from the other end of the outer peripheral inclined portion 212. The outer peripheral inclined portion 212 and the outer peripheral 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° apart from the outer circumferential inclined portion 212 in the circumferential direction. One end of the inner circumferential inclined portion 214 is connected to the flat portion 211, and the inner circumferential inclined portion 214 is an inclined surface that is inclined from the flat portion 211 so that it slopes rearward as it moves clockwise in a front-to-back view. The inner circumferential inclined portion 214 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 and 219 engage (fit) with the anti-rotation projections 148 and 149 of the gear case 140 described above, making 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 peripheral projection 232, an inner peripheral projection 234, and two locking projections 235.

[0069] The outer peripheral protrusion 232 protrudes rearward from the radially outer portion of the front stopper cam ring 230. The outer peripheral protrusion 232 is a flat or curved plate-like portion that is approximately perpendicular to the radial direction. The radial position of the outer peripheral protrusion 232 is the same as 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 peripheral projection 234 projects rearward from the radially inner portion of the front stopper cam ring 230. The inner peripheral projection 234 is a flat or curved plate-like portion that is approximately perpendicular to the radial direction. The inner peripheral projection 234 is located approximately 180° apart from the outer peripheral projection 232 in the circumferential direction. The radial position of the inner peripheral projection 234 is the same as the radial positions of the inner peripheral inclined portion 214 and the inner peripheral 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 about 180° apart 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 14(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 the threaded portion 301 of the clutch dial 300, which will be described later. The six spring locking holes 262 are non-through holes arranged at equal angular intervals in the circumferential direction, and each holds the front end of the clutch spring 250 (made of metal, for example) shown in Figures 5 to 7. The three notches 263 are arranged at equal angular intervals in the circumferential direction, and each receives a screw 133 shown in Figures 5 to 7.

[0075] 6 and 7 is made of, for example, metal, and is urged rearward by clutch spring 250 against nut 260, pressing the front end of clutch pin 131 rearward and forcing 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, passing 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 15(G), ratchet cam ring 280 has an outer circumferential projection 282, an inner circumferential projection 284, three anti-rotation projections 285, and three small projections 288. As shown in FIGS.

[0078] The outer peripheral projection 282 projects forward from the 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 the 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 gap between the two-pronged anti-rotation portions 144 of the gear case 140 described above. This prevents the ratchet cam ring 280 from rotating 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 peripheral 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 and the circumferential position of the outer protrusion 372 of the clutch hub 370 coincide, and serve to determine circumferential positioning.

[0082] When setting ratchet cam ring 280 in front of clutch hub 370, outer protrusion 372 of clutch hub 370 is passed through the gap in the circumferential direction between anti-rotation protrusion 285 and small protrusion 288. Then, ratchet cam ring 280 is rotated until small protrusion 288 contacts the outer peripheral surface of thread boss portion 345 of front case 340, and the biasing force of ratchet spring 360 brings the back surface of anti-rotation protrusion 285 into contact with the front surface of outer protrusion 372 of 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 Figures 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 mounting 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 that is generally circular, and a diameter that decreases toward the front. The front wall portion 307 extends radially inward from the front end 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 is threadedly engaged with the threaded portion 261 of the nut 260 described above. The clutch dial 300 is sandwiched in the front-rear direction between the gear case 140 and a front case 340 described below, 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 approximately 180° apart in the circumferential direction, and are each formed as a notch formed by partially cutting out the lower end of threaded portion 301. Locking recesses 302 engage with locking protrusions 235 of front stopper cam ring 230 described above, causing front stopper cam ring 230 to rotate together with clutch dial 300.

[0088] The inner recess 304 is located on the radially inner portion of the back surface of the front wall 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 (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 the 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 to which a leaf spring 331 (made of metal, for example) that appears in FIGS. 6 and 7 is attached.

[0091] The transmission / output component 4 includes a front case 340 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 a large diameter cylindrical portion 341, a small diameter cylindrical portion 342, a connection surface portion 343, three notches 344, three screw boss portions 345, three screw holes 346, three screw holes 347, a bearing holding portion 348, two anti-rotation protrusions 349, two anti-detachment protrusions 350, and a 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 connecting surface portion 343 is a wall portion perpendicular to the front-rear direction that connects the rear end of the large-diameter cylindrical portion 341 and the front end of the small-diameter cylindrical portion 342.

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

[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 threadedly fitted 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 rotatably supports the rear portion of the spindle 470.

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

[0097] The two retaining projections 350 are located approximately 180° apart from each other in the circumferential direction, and protrude radially outward from the left and right portions of the outer circumferential surface of the large-diameter cylindrical portion 341, respectively. The protruding length of the retaining projections 350 is shorter than the protruding length of the anti-rotation projections 349. The retaining projections 350 are continuous with the anti-rotation projections 349 on both sides in the circumferential direction. The retaining projections 350 prevent the sub-handle 600, which will be described later, 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 ones corresponding to each stage of the set tightening torque for the clutch mode, ones corresponding to the drill mode, and ones 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, preventing 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 18(E), the clutch hub 370 has an annular portion 371, three outer protrusions 372, and six locking projections 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 are protrusions that each protrude radially inward from the rear 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 concave and convex 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, for example, metal, and are interposed between the back surface of the rear ratchet 410 and the opposing surface of the front case 340 to receive a load in the front-to-rear direction. The thrust bearing 391 and bearing washer 395 reduce friction and suppress power loss when the 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 rear 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 relative to it.

[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 the mating member, the rear ratchet 410 and the front ratchet 440 are not in contact with each other, thereby suppressing the generation of vibration. 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 relative 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 integrally with the spindle 470.

[0111] The threaded portion on the inner peripheral surface of the rear of the chuck 500 is threadedly engaged with the 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 constitute a substantially integrated tool holder.

[0112] Bearing cover 485 shown in FIGS. 5 to 7 is made of metal, for example, and is fixed to front case 340 by screws 489 that 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, which appears in FIGS. 5 to 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 rotation is stopped (when braking). O-ring 481 also functions to prevent oil leakage.

[0114] 5 to 7 is made of metal, for example, 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 coming off.

[0115] (Disassembly of transmission and 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 various parts (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 arranged 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 by it.

[0118] The output section 7 includes a front case 340 and the components held or supported by it, that is, the spindle 470, the chuck 500, the 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 threaded holes 347 of the front case 340.

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

[0121] When the transmission unit 5 is removed from the output unit 7, that is, when the screw 133 is 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 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., the clutch mechanism is active. The set tightening torque can be adjusted in multiple stages, for example, 22 stages, by operating the clutch dial 300.

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

[0125] The clutch mechanism stops rotation of the final ring gear 90 up to a set tightening torque, but allows 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] If a load (torque) is applied to the bit 20 while the motor 30 is running, the loose final ring gear 90 will tend 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 prevents the final ring gear 90 from rotating, and torque transmission by the transmission mechanism 50 is enabled.

[0127] On the other hand, when the torque applied to the bit 20 increases and exceeds the set tightening torque, that is, when a load (torque) greater than the force that causes the clutch pin 131 to push the final ring gear 90 rearward 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 moves over 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 clutch spring 250. When clutch dial 300 is turned, nut 260 moves back and forth, and the amount of compression of clutch spring 250 can be changed.

[0129] 23(A) to 23(E), nut 260 is in the most advanced position, and the amount of compression of clutch spring 250 is minimum (set tightening torque is 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) to 24(E), nut 260 is in the most advanced position, and the amount of compression of clutch spring 250 is maximum (set tightening torque is highest).

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

[0131] From the state shown in Figures 24(A) to (E), i.e., the state in which the clutch mode and the set tightening torque are set to the maximum, if the clutch dial 300 is further rotated clockwise as viewed from the front to a rotation position corresponding to the drill mode, the state will become as 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 (forward position) and a non-locking position (rearward position), and when in the locking position, it prevents the final ring gear 90 from rotating. 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 urges 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 can rotate 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 restricting portions that restrict movement of the stopper block 120 from the unlocked position to the locked position against the biasing force 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 being restricted and being released 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 unlocked position and the locked position in conjunction with the rotation of the clutch dial 300.

[0136] The rear stopper cam ring 210 is located forward 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 anti-rotation portion protrusions 148, 149 of the gear case 140 and the anti-rotation 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 unlocked position to the locked position.

[0138] Rear stopper cam ring 210 has outer peripheral inclined portion 212 and outer peripheral flat portion 213 as recesses, and inner peripheral inclined portion 214 and inner peripheral flat portion 215 as recesses. Front stopper cam ring 230 has outer peripheral protrusion 232 and inner peripheral protrusion 234 as protrusions. As front stopper cam ring 230 reaches a predetermined rotation position (as clutch dial 300 reaches the rotation position for drill mode), outer peripheral protrusion 232 and inner peripheral protrusion 234 descend outer peripheral inclined portion 212 and inner peripheral inclined portion 214, and rear stopper cam ring 210 moves forward. The slopes of outer peripheral inclined portion 212 and inner peripheral inclined portion 214 are preferably steeper than the slope of thread portion 301 of clutch dial 300.

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

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

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

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

[0143] The drill mode switching configuration 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 unit that moves from a vibration-off position (retracted position) to a vibration-on position (advanced position) in response to operation of the clutch dial 300. The ratchet spring 360 is made of, for example, metal, and is a biasing unit 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 the ratchet cam ring 280 shown in Figures 15(A) to (E) and (G), and the inner peripheral recess 304 and outer peripheral hole 305 of the clutch dial 300 shown in Figures 16(A) to (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 the clutch dial 300 reaches 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 outer peripheral hole 305 and inner peripheral recess 304 of clutch dial 300, respectively, and the urging force of ratchet spring 360 moves ratchet cam ring 280 and clutch hub 370 from the vibration-off position to the vibration-on position.

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

[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, it restricts the movement of the rear ratchet 410. Vibration occurs 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, pressing forward ratchet cam ring 280. Locking protrusion 373 of clutch hub 370, which appears in Figures 18(A) to (D), and locking protrusion 412 of rear ratchet 410, which appears in Figures 19(A) to (C) and (E) to (F), engage with each other as shown in Figures 22(C) and 26(D) when clutch hub 370 is in the vibration-on position.

[0151] As shown in Figures 22(B) and (C), inclined portions 374, 413 are provided on both circumferential sides of the locking protrusion 373 of the clutch hub 370 and the locking protrusion 412 of the rear ratchet 410 to prevent the clutch hub 370 from moving 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-to-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 rotational force is applied to the rear ratchet 410 in this state, the engagement of the inclined portions 374, 413 applies a forward force to the clutch hub 370, making it difficult for the clutch hub 370 to move to the vibration-off position.

[0152] 25(A) to 25(E) and 26(A) to 26(E) show that, during 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 become aligned. During this process, outer peripheral projection 232 and inner peripheral projection 234 of front stopper cam ring 230 move over outer peripheral flat portion 213 and inner peripheral 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 predetermined rotation range corresponding to the aforementioned clutch mode and drill mode (a rotational position between the states of Figures 23(A) to (E) and 25(A) to (E)), the outer peripheral protrusion 282 and inner peripheral protrusion 284 of the ratchet cam ring 280 abut against the flat portion (flat portion perpendicular to the front-to-rear direction) of the clutch dial 300, and the ratchet cam ring 280 and clutch hub 370 do not move forward (do not move to the vibration on position).

[0154] (How to thread the shift arm 71) As described above, the motor spacer 40, rear case 60, and gear case 140 are fixed together with four screws 44 to form the transmission housing. This increases the rigidity of the entire transmission housing, and can 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 extends to the guide hole 64 of the rear case 60.

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

[0158] The two upper screws 44 have portions extending in the front-to-rear direction outside the rear case 60 that are inserted into threaded collars 45, which are cylindrical portions separate from the rear case 60. That is, the two upper screws 44 each pass through the screw insertion holes 43 and the threaded collars 45 of the motor spacer 40, and are threaded into the threaded holes 151 of the gear case 140. The threaded collars 45 are used to prevent the motor spacer 40 from being bent or damaged due to overtightening of the two upper screws 44. The shift arm 71 passes through the gap between the outer circumferential surface of the threaded collars 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-holes 67 of the rear case 60, respectively, and are screwed into the threaded holes 151 of the gear case 140. The screw boss portion 62 having the through-holes 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 the part through which the shift arm 71 passes, so there is no problem of an increase in size or the like.

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

[0161] (Opening and closing structure of the mount 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 part 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 (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 portion holding portion 624 and a shaft portion insertion portion 626. The head portion holding portion 624 holds the head 610 of the first shaft portion 602. The head portion holding portion 624 is located on one side of the shaft portion insertion portion 626 in the length direction of the gap (the left side in FIG. 35 ), and is larger and non-circular, for example hexagonal, than the shaft portion insertion portion 626 when viewed from the length direction of the gap, into which the head 610 fits. The shaft portion insertion portion 626 is smaller than the head portion 610 when viewed from the length direction of the gap, and the shaft portion 611 of the first shaft portion 602 passes.

[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 ) of the shaft portion insertion portion 627, has a larger diameter than the shaft portion insertion portion 627, and allows the shaft portion 611 of the first shaft portion 602 to pass through it and also inserts the end of the second shaft portion 603 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 lengths longer than the natural length. The natural length is the length of the gap 614 when 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 attached to 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 length direction of the gap and is provided on the mount portion 601 on the other side of the gap 614 in the length direction of the gap (the right side in FIG. 35) so as to be immovable in the length direction. The second shaft portion 603 protrudes from the mount portion 601 to the other side in the length 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 relative 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 in the gap length direction. The head portion 610 fits into a head portion holding portion 624 of the mount portion 601, preventing the first shaft portion 602 from rotating relative to the mount portion 601 and preventing the first shaft portion 602 from slipping 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 the 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 and 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 peripheral 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 mount 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 run 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 frictional resistance to 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 forms 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 Figure 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 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, engagement between the second shaft portion 603 and the second cylindrical portion 613 of the mount portion 601 via the pin 607 moves the second cylindrical portion 613 in the gap length direction relative to the first cylindrical portion 612. This adjusts the length of the gap 614.

[0182] 38(B) and (E), i.e., when gap 614 is at its natural length, by turning grip portion 604 to the left, 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 gap 614 can be adjusted to be longer than its natural length. FIGS. 38(C) and (F) show the state when gap 614 is at its maximum length, i.e., the state when mount portion 601 is fully opened. 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 will not damage mount portion 601.

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

[0184] By opening the gap 614 wider than its natural length, the front case 340 of the work implement 1 can be passed inside the mount part 601. The anti-slip protrusion 350 of the front case 340 is large enough that it 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 out of the front case 340 when the gap 614 is at or below its natural length.

[0185] (Easy storage structure of sub-handle 600) To attach the sub-handle 600 to the front case 340, adjust the length of the gap 614 to be longer than its natural length, and then fit the mount part 601 into the front case 340 from the front. Then, turn the grip part 604 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 multiple 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.

[0187] The circumferential length of the first anti-rotation recess 616 of the mount part 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 part 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 the sub-handle 600 can be attached to the front case 340 without or with minimal rattle. 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 implement 1 is in use.

[0189] When the first anti-rotation recess 616 of the mount portion 601 and the anti-rotation protrusion 349 of the front case 340 are engaged with each other, the circumferential length of the first anti-rotation recess 616 is longer than the circumferential length of the anti-rotation protrusion 349, and therefore 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 implement 1 is not in use.

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

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

[0192] 39(B) shows a state in which the sub-handle 600 is in the center of its rotatable range. This state is a second engagement state in which the circumferential ends of the first anti-rotation recessed portion 616 of the mount portion 601 and 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 circumferential ends of the first anti-rotation recessed portion 616 of the mount portion 601 and the anti-rotation protrusion 349 of the front case 340 may also engage with each other.

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

[0194] This embodiment has the following advantages.

[0195] (1) The work machine 1 includes an output switching unit 6 that switches the output (torque and presence or absence of vibration) of the output unit 7, and is 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 screws 133 are removed and the gear case 140 is removed from the front case 340 (removing the transmission unit 5 from the output unit 7), the output switching unit 6 can be removed rearward from the output unit 7. Therefore, even if the spindle 470 and the chuck 500 cannot be released from their fixed positions, the components of the output switching unit 6, i.e., the clutch dial 300, the nut 260, the clutch spring 250, and other parts, can be replaced, resulting in good repairability.

[0196] For comparison, consider a configuration in which gear case 140 is extended forward, ball bearings 335, 461 are held, and a retaining ring prevents clutch dial 300 from slipping out of gear case 140 in the forward direction (hereinafter referred to as "Comparative Configuration 1"). In Comparative Configuration 1, the retaining ring cannot be accessed unless chuck 500 is removed from spindle 470, and clutch dial 300 and other components cannot be removed forward or backward. Therefore, in Comparative Configuration 1, if clutch dial 300 and other components are damaged and need to be replaced, it is necessary to remove chuck 500 from spindle 470 using a special jig or replace the entire transmission / output component 4, which increases the time and cost required for repairs. This embodiment is intended to suitably solve such problems.

[0197] (2) The transmission unit 5 and the output unit 7 can be used as modules in common with multiple models, which is highly convenient.

[0198] (3) The work machine 1 includes a transmission mechanism 50 including the final ring gear 90, a stopper block 120 that disables the rotation of the final ring gear 90 when the stopper block 120 is in the locked position, and a stopper spring 117 that urges the stopper block 120 toward the locked position. Therefore, even if the front end of the protrusion 123 of the stopper block 120 that is attempting to move to the locked position comes into contact with the rear end of the outer peripheral protrusion 91 of the final ring gear 90, preventing the stopper block 120 from reaching the locked position, if the final ring gear 90 subsequently rotates, the outer peripheral protrusion 91 will move from in front of the protrusion 123, and the stopper block 120 will automatically move to the locked position. This makes it possible to prevent a malfunction that makes it impossible to disable the rotation of the final ring gear 90, i.e., a malfunction that makes it impossible to switch to 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 using the clutch dial 300. Specifically, when the clutch dial 300 is rotated to the drill mode rotation position, the stopper block 120 moves to the 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 a result of thread engagement that utilizes 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, which moves back and forth in conjunction with the rotation of the clutch dial 300, this configuration can prevent problems that make it impossible to rotate the clutch dial 300 to the drill mode rotation position, and is easier to use.

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

[0201] (6) When clutch dial 300 is within the rotation range of the clutch mode, rear stopper cam ring 210 and front stopper cam ring 230 function as a restriction portion that restricts movement of stopper block 120 from the unlocked position to the locked position against the biasing force of stopper spring 117. Furthermore, rear stopper cam ring 210 and front stopper cam ring 230 form a cam mechanism that moves stopper block 120 between the unlocked position and the locked position in conjunction with rotation of clutch dial 300 between the drill mode rotation position and the clutch mode rotation position. Therefore, the forward and backward movement of stopper block 120 is limited to when clutch dial 300 rotates between the drill mode rotation position and the clutch mode rotation position, and the forward and backward movement of stopper block 120 (movement between the unlocked position and the locked position) can be suitably achieved without relying on threaded engagement between clutch dial 300 and nut 260.

[0202] (7) When clutch dial 300 rotates between the drill mode rotation position and the clutch mode rotation position, outer peripheral protrusion 232 and inner peripheral protrusion 234 of front stopper cam ring 230 move along outer peripheral inclined portion 212 and inner peripheral inclined portion 214 of rear stopper cam ring 210. Here, by making the inclination angles of outer peripheral inclined portion 212 and inner peripheral inclined portion 214 steeper than the inclination of thread portion 301 of clutch dial 300, stopper block 120 can be moved significantly forward and backward in conjunction with the rotation of clutch dial 300, compared to when stopper block 120 is moved by threaded engagement between clutch dial 300 and nut 260. This reduces the amount of operation of clutch dial 300 required to switch between clutch mode and drill mode, improving usability. Furthermore, because 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 move in and out of the recess. This reduces sticking 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 and engages with the rear stopper cam ring 210. As a result, the configuration for switching to the drill mode (stopper block 120, stopper spring 117, rear stopper cam ring 210, front stopper cam ring 230) is distributed and disposed in front of and behind the final ring gear 90. Therefore, unlike when the configuration for switching to the drill mode is biasedly disposed either in front of or behind the final ring gear 90, it is easier to balance the radial sizes of the gear case 140 and the clutch dial 300, and layout efficiency is good.

[0204] (9) In the work machine 1, when the clutch hub 370 reaches the vibration-on position, the clutch hub 370 restricts the movement of the rear ratchet 410. Vibration occurs when the front ratchet 440 is driven by the driving force of the motor 30 relative to the restricted movement of the rear ratchet 410. When the clutch dial 300 reaches a rotational position corresponding to the vibration mode, the outer peripheral protrusion 282 and the inner peripheral protrusion 284 of the ratchet cam ring 280 move along their respective inclined portions 286 and 287 into the outer peripheral hole 305 and the inner peripheral recess 304 of the clutch dial 300, 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, which 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 the vibration on and off can be reduced, providing improved usability.

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

[0206] (11) When the clutch dial 300 is within the rotation ranges of the clutch mode and drill mode, the ratchet cam ring 280 and the clutch dial 300 function as a restriction portion that restricts 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. Furthermore, the ratchet cam ring 280 and the clutch dial 300 form 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 (movement between the vibration-off position and the vibration-on position) 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 can be suitably achieved 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), both circumferential sides of the locking protrusion 373 of the clutch hub 370 and the locking protrusion 412 of the rear ratchet 410 are provided with 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. When a rotational force is applied to the rear ratchet 410 in the vibration-on position, the engagement between the inclined portions 374, 413 applies a forward force to the clutch hub 370, making it difficult for it to move to the vibration-off position. This prevents the clutch hub 370 from accidentally moving to the vibration-off position due to vibrations, etc.

[0208] (13) The motor spacer 40, rear case 60, and gear case 140 are fixed with four screws 44 to form a highly rigid transmission housing, 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 this gap to the guide hole 64 of the rear case 60. Therefore, compared to a configuration in which the shift arm 71 passes outside the screws 44 in the radial direction of the rear case 60 and extends 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, thereby suppressing an increase in size of the product.

[0209] (14) The two upper screws 44 have portions extending in the front-rear direction outside the rear case 60 that are inserted into thread collars 45, which are cylindrical portions 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 protrusion 350 for preventing the sub-handle 600 from slipping out, which prevents the sub-handle 600 from slipping out forward due to vibrations during work, improving workability.

[0211] (16) The sub-handle 600 is annular with a gap 614 in part of its circumferential direction 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 lengths longer than the natural length. Therefore, even if the length of the gap 614 in the front case 340 is in its natural length and interferes with, for example, the retaining protrusion 350 of the front case 340, making attachment and detachment difficult, attachment and detachment can be easily achieved by adjusting the length of the gap 614 to be longer than the natural length.

[0212] (17) The first shaft portion 602 and the second shaft portion 603 are threadedly engaged with each other, and the length of the gap 614 can be adjusted by turning the grip portion 604 provided on the second shaft portion 603. Therefore, the length of the 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. Because the pin 607 allows the second shaft portion 603 to rotate, the length of the gap 614 can be adjusted without being prevented from being 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 easily rotating, improving workability.

[0215] (20) 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 that will not damage the mount portion 601. Therefore, regardless of the degree of operation by the user, damage to the mount portion 601 due to excessive widening of the gap 614 can be suppressed, resulting in good usability.

[0216] (21) The mount portion 601 has a first anti-rotation recess 616 that is long in the circumferential direction and a second anti-rotation recess 617 that is short in the circumferential direction. When the second anti-rotation recess 617 and the anti-rotation protrusion 349 of the front case 340 are engaged with each other, their circumferential lengths are approximately equal. This allows the sub-handle 600 to be attached to the front case 340 without or with minimal rattle, 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, the circumferential length of the first anti-rotation recess 616 is longer than the circumferential length of the anti-rotation protrusion 349. This allows the sub-handle 600 to be rotated within a predetermined angle range relative to the work implement 1 in the stored state, as shown in FIGS. 39(A) and (C). This allows for fine adjustment of the attached state. This improves the ease of storing the sub-handle 600 in the work implement 1. 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, but this embodiment can suitably solve such problems.

[0217] (22) Even when the first anti-rotation recess 616 of the mount 601 and the anti-rotation protrusion 349 of the front case 340 are engaged with each other, by setting the gap 614 of the mount 601 to a predetermined length that is shorter than the natural length, the frictional force generated when the mount 601 tightens against the front case 340 can prevent the sub-handle 600 from rotating relative to the front case 340. This makes it possible to suppress rattle of the sub-handle 600 in the stored state as needed. Furthermore, even when the first anti-rotation recess 616 of the mount 601 is configured to be used when the work implement 1 is in use, rattle during work can be suppressed.

[0218] Although the present invention has been described above using the embodiments as examples, the present invention is not limited to the embodiments. Various modifications can be made to the details specifically described in the embodiments within the scope of the claims.

[0219] The concave-convex structure exemplified in the embodiment may have the concave-convex relationship reversed as appropriate. For example, rear stopper cam ring 210 may have a convex portion, and front stopper cam ring 230 may have a concave portion that engages with the convex portion. Similarly, ratchet cam ring 280 may have a concave portion, and clutch dial 300 may have a convex portion that engages with the concave portion.

[0220] The number of outer peripheral protrusions 91 of the final ring gear 90 and stopper blocks 120, the number of screws 44, 133, the number of set tightening torque levels, the number of possible angles at which the sub-handle 600 can be attached 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 embodiments, 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 selector switch, 20...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 holder 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 convex 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 peripheral convex portion, 92...cylindrical portion, 93...flange portion, 94...gear portion, 95...front convex 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...Latching 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...Anti-rotation 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 protrusion, 234...inner peripheral side protrusion, 235...locking protrusion, 250...clutch spring, 260...nut, 261...threaded portion,262...spring locking hole, 263...notch, 280...ratchet cam ring, 282...outer peripheral protrusion, 284...inner peripheral protrusion, 285...rotation prevention protrusion, 286...inclined portion, 287...inclined portion, 288...small protrusion, 300...clutch dial, 301...threaded portion, 302...locking recess, 304...inner peripheral recess, 305...outer peripheral hole, 306...cylindrical portion, 307...front wall portion, 308...leaf spring mounting portion, 331...leaf spring, 335...ball bearing (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 holding portion, 349...rotation prevention protrusion portion (rotation restriction portion), 350...retaining protrusion portion, 351...locking recess portion, 360...ratchet spring, 370...clutch hub, 371...annular portion, 372...outside protrusion portion, 373...locking protrusion portion, 374...inclined portion, 391...thrust bearing, 395...bearing washer, 410...rear ratchet, 411...uneven portion (vibration prevention portion) generating shape portion), 412...engaging convex portion, 413...inclined portion, 431...spring, 435...ratchet washer, 440...front ratchet, 441...concave and concave 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 portion, 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 tool holder driven by the motor; a vibration unit that outputs the driving force of the motor to the tool bit holder as vibration; a switching operation unit that switches between a vibration-on state and a vibration-off state of the vibration unit; a vibration switching unit that moves from a vibration off position to a vibration on position in response to an operation of the switching operation unit, a guide unit that guides the vibration switching unit to move from the vibration-off position to the vibration-on position when the switching operation unit reaches a predetermined position, the guide portion includes a recess or a hole provided in one of the switching operation portion and the vibration switching portion and a protrusion provided in the other of the switching operation portion and the vibration switching portion, a biasing portion that biases the vibration switching portion in a direction in which the convex portion enters the concave portion or the hole portion, When the switching operation unit reaches a predetermined position, the recess or hole and the protrusion face each other, and the protrusion enters the recess or hole, and the vibration switching unit moves from the vibration-off position to the vibration-on position due to the biasing force of the biasing unit. A work machine characterized by:

2. the vibration unit includes a first vibration unit driven by a driving force of the motor and a second vibration unit engaged with the first vibration unit, the vibration switching unit does not engage with the second vibration unit at the vibration-off position, and engages with the second vibration unit at the vibration-on position to restrict rotation of the second vibration unit; The concave-convex portion of the first vibrating part is driven by the driving force of the motor with respect to the concave-convex portion of the second vibrating part whose rotation is restricted, and the concave-convex portion of the first vibrating part and the concave-convex portion of the second vibrating part come into contact with each other and rotate relative to each other, thereby generating vibration.

2. The work machine according to claim 1.

3. the vibration switching unit and the second vibration unit each have a locking protrusion that can be engaged with each other, The vibration switching unit and the locking protrusion of the second vibration unit are each provided with an inclined portion that makes it difficult for the vibration switching unit to move to the vibration-off position when a force in a rotational direction is applied to the second vibration unit.

3. The work machine according to claim 2.

4. The vibration switching unit a ratchet cam ring having the protrusion, the recess, or the hole; a clutch hub that is biased by the biasing portion in a direction pressing the ratchet cam ring and that restricts movement of the second vibration portion at the vibration-on position.

3. The work machine according to claim 2.

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