Work equipment

Abstract

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

Description

Technical Field

[0001] The present invention relates to a working machine.

Background Art

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

[0003] A working machine such as a driver drill includes a motor, a spindle, a transmission mechanism for transmitting the rotation of the motor to the spindle, a chuck screwed onto the spindle, a reduction ratio switching mechanism for switching the reduction ratio of the transmission mechanism, and a clutch mechanism for blocking the rotation transmission from the transmission mechanism to the spindle at a predetermined torque.

[0004] The reduction ratio switching mechanism has a shift knob operated by a user and a shift arm for advancing and retreating a sliding ring gear of the transmission mechanism in conjunction with the operation of the shift knob. The clutch mechanism has a clutch dial for a user to change a predetermined torque. A driver drill having a vibration function as in Patent Document 2 is also called a vibration driver drill, and the presence or absence of vibration can also be switched by operating the clutch dial. [[ID=XXX]] [[ID=XXX]] [[ID=2X]]

Prior Art Documents

[0005] [[ID=XXX]] [[ID=XXX]]

Patent Document 1

Patent Document 2

Patent Document 3

Summary of the Invention

Problems to be Solved by the Invention

[0006] [[ID=XXX]] It should be noted that there are some tags with "XXX" in the original that seem to be mislabeled or incomplete in the numbering. I've translated as accurately as possible based on the available content.In power tools such as driver drills, the chuck and spindle are fixed with high torque, and a special tool is required to release the fixation. In other words, without a special tool, the chuck and spindle essentially become a single tool holder. As a result, it was difficult to replace parts that could not be removed without releasing the fixation of the chuck and spindle. Conventional power tools had many parts that were difficult to replace, resulting in poor repairability. The first problem identified by the inventor was to provide a power tool with good repairability.

[0007] In drilling tools such as driver drills, the torque is maximized in drill mode by fixing the ring gear of the transmission mechanism so that it cannot rotate. One configuration for entering drill mode involves a nut that rotates with the clutch dial and moves axially, pushing a stopper pin towards the ring gear. However, depending on the rotational position of the ring gear, a part of the ring gear may be in the extension of the stopper pin. In the above configuration, if the stopper pin hits this part, the clutch dial cannot be turned, preventing the tool from entering drill mode, resulting in poor usability. The second problem identified by the inventor is to provide a drilling tool that can suppress the problem of being unable to fix the ring gear in a non-rotatable position.

[0008] In a power tool such as a driver drill, where the transmission mechanism is housed in multiple cases separated in the front-to-back direction, the rigidity of the cases can be increased and deformation suppressed by fixing the multiple cases in the front-to-back direction with fasteners such as screws. However, in a configuration where the shift arm passes outside the fasteners in the radial direction of the case, the product becomes larger in the radial direction. The third problem identified by the inventor is to provide a power tool that can suppress this increase in size.

[0009] In power tools such as rotary hammer drills, if the amount of clutch dial operation required to switch between vibration on and off is large, switching between vibration on and off becomes cumbersome and work efficiency is poor. The fourth problem identified by the inventor is to provide a power tool that can reduce the effort required to switch between vibration on and off.

[0010] A known configuration for a handle that can be attached to and detached from a work implement involves attaching the handle to the implement by closing the gap in an annular mounting portion that has a gap (opening) in a part of the circumferential direction. In this configuration, if the maximum length of the gap in the mounting portion is the natural length, it can be difficult to attach and detach the handle. The fifth problem identified by the present inventor is to provide a handle that is easy to attach and detach from a work implement, and a work implement equipped with such an easy-to-attach handle.

[0011] If the handle cannot be moved while attached to the implement, it is inconvenient because the attachment state of the handle cannot be finely adjusted. The sixth problem identified by the inventor is to provide a handle that allows for fine adjustment of the attachment state to the implement, and an implement equipped with a handle that allows for fine adjustment of the attachment state.

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

[0013] One aspect of the present invention is a work machine. This work machine is Motor and, A reduction mechanism having a ring gear for reducing the rotation of the motor, A stopper portion that is movable between a locked position and an unlocked position, and which prevents the ring gear from rotating when it is in the locked position, A biasing means for biasing the stopper portion toward the locking position, A clutch dial operated by the operator to adjust the set tightening torque, The device includes a clutch mechanism that stops the rotation of the ring gear until the set tightening torque is reached, and allows the rotation of the ring gear once the set tightening torque is exceeded, A work machine that allows selection of at least one of the following modes: a clutch mode in which the clutch mechanism allows the ring gear to rotate when the set tightening torque is exceeded, and a drill mode in which the ring gear is prevented from rotating by the clutch mechanism, The clutch dial is configured and includes a switching operation unit that can switch the position of the stopper portion between the locked position and the unlocked position. When the clutch mode is selected, the stopper portion is Non In the locked position, the stopper portion does not engage with the ring gear in the rotational direction. When the switching operation unit is operated to a predetermined position corresponding to the drill mode from the state in which the clutch mode is selected, the stopper unit moves due to the biasing of the biasing means. Non The device is configured to move from the locked position to the locked position, the stopper portion engages with the ring gear in the rotational direction, and the device switches to the drill mode. Another aspect of the present invention is a work machine. This work machine is Motor and, A reduction mechanism having a planetary gear mechanism including planetary gears and ring gears, which reduces the rotation of the motor, A spindle, which is rotationally driven by the motor via the reduction mechanism and rotates integrally with the chuck that holds the tip tool, A clutch dial operated by the operator to adjust the set tightening torque, The device includes a clutch mechanism that stops the rotation of the ring gear until the set tightening torque is reached, and allows the rotation of the ring gear once the set tightening torque is exceeded, A work machine that allows selection of at least one of the following modes: a clutch mode in which the clutch mechanism allows the ring gear to rotate when the set tightening torque is exceeded, and a drill mode in which the ring gear is prevented from rotating by the clutch mechanism, A stopper portion is movable between a locked position and an unlocked position, and when in the locked position, it engages with the ring gear in the rotational direction to prevent the ring gear from rotating, while when in the unlocked position, it does not engage with the ring gear in the rotational direction and allows the ring gear to rotate. A switching operation unit that allows the operator to switch the position of the stopper between the locked position and the unlocked position, A biasing means for biasing the stopper portion toward the locking position, A restricting part that can restrict the movement of the stopper part from the non-locking position to the locking position against the biasing of the biasing means, and by operating the switching operation part, whether to restrict the movement of the stopper part from the non-locking position to the locking position, or to release the restriction on the movement of the stopper part from the Non locking position to the locking position is switched, and a restricting part is provided. When the switching operation part is operated to a predetermined position corresponding to the drill mode from the state where the clutch mode is selected, the restriction on the movement of the stopper part by the restricting part from the Non locking position to the locking position is released, and the stopper part moves from the Non locking position to the locking position by the biasing of the biasing means, and the stopper part engages with the ring gear in the rotational direction, and is configured to switch to the drill mode.

[0014] The present invention may be expressed as "electric working machine", "electric tool", "electrical equipment", etc., and those expressed as such are also effective as aspects of the present invention.

Effect of the Invention

[0015] According to the present invention, it is possible to provide a working machine that solves at least the second problem among the above problems.

Brief Description of the Drawings

[0016] [Figure 1] Perspective view of the working machine 1 according to the embodiment of the present invention as viewed from the front side. [[ID=]28] [Figure 2] Perspective view of the working machine 1 as viewed from the rear side. [Figure 3] Right side view of the working machine 1. [[.END]] [Figure 4] Right side cross-sectional view of the working machine 1. [Figure 5] Enlarged right side cross-sectional view showing the configuration of the transmission / output configuration part 4 of the working machine 1. [Figure 6] Exploded perspective view of the transmission / output configuration part 4 as viewed from the front side. [Figure 7]This is an exploded perspective view of the transmission / output component 4, viewed from the rear. [Figure 8] (A) is a perspective view of the rear case 60 shown in Figures 5 to 7, viewed from the front. (B) is a perspective view of the rear case 60, viewed from the rear. (C) is a front view of the rear case 60. (D) is a cross-sectional view of AA in Figure 8(C). (E) is a cross-sectional view of 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 shown in Figures 5 to 7, viewed from the front. (B) is a perspective view of the final ring gear 90, viewed from the rear. (C) is a front view of the final ring gear 90. (D) is a cross-sectional view of AA in Figure 9(C). (E) is a cross-sectional view of 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] (A) to (D) are perspective views of the stopper block 120 shown in Figures 5 to 7, viewed from different viewpoints. (E) is a front view of the stopper block 120. (F) is a cross-sectional view of AA in Figure 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] (A) is a perspective view of the gear case 140 as shown in Figures 5 to 7. (B) is a front view of the gear case 140. (C) is a cross-sectional view of AA in Figure 11(B). (D) is a rear view of the gear case 140. (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 shown in Figures 5 to 7, viewed from the front. (B) is a perspective view of the rear stopper cam ring 210, viewed from the rear. (C) is a front view of the rear stopper cam ring 210. (D) is a cross-sectional view of AA in Figure 12(C). (E) is a cross-sectional view of 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 shown in Figures 5 to 7, viewed from the front. (B) is a perspective view of the front stopper cam ring 230, viewed from the rear. (C) is a front view of the front stopper cam ring 230. (D) is a cross-sectional view of AA in Figure 13(C). (E) is a cross-sectional view of 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] (A) is a perspective view of the nut 260 as shown in Figures 5 to 7. (B) is a front view of the nut 260. (C) is a cross-sectional view AA of Figure 14(B). (D) is a rear view of the nut 260. (E) is a right side view of the nut 260. [Figure 15] (A) is a perspective view of the ratchet cam ring 280 shown in Figures 5 to 7, viewed from the front. (B) is a perspective view of the ratchet cam ring 280, viewed from the rear. (C) is a front view of the ratchet cam ring 280. (D) is a cross-sectional view of AA in Figure 15(C). (E) is a cross-sectional view of 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, viewed from the front. (B) is a perspective view of the clutch dial 300, viewed from the rear. (C) is a front view of the clutch dial 300. (D) is a cross-sectional view of 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] (A) is a perspective view of the front case 340 as shown in Figures 5 to 7. (B) is a front view of the front case 340. (C) is a cross-sectional view AA of Figure 17(B). (D) is a rear view of the front case 340. (E) is a right side view of the front case 340. [Figure 18] (A) is a perspective view of the clutch hub 370 as shown in Figures 5 to 7. (B) is a front view of the clutch hub 370. (C) is a cross-sectional view AA of 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](A) is a perspective view of the rear ratchet 410 shown in Figures 5 to 7, viewed from the front. (B) is a perspective view of the rear ratchet 410, viewed from the rear. (C) is a front view of the rear ratchet 410. (D) is a cross-sectional view of AA in Figure 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] (A) is a perspective view of the front ratchet 440 shown in Figures 5 to 7, viewed from the front. (B) is a perspective view of the front ratchet 440, viewed from the rear. (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 of AA in Figure 20(E). [Figure 21] A right-side cross-sectional view showing the transmission / output component 4 separated into the transmission unit 5, output switching unit 6, and output unit 7. [Figure 22] (A) is a view of the clutch hub 370 and rear ratchet 410 from the front. (B) is a cross-sectional view AA of Figure 22(A), showing the positional relationship between the locking projection 373 of the clutch hub 370 and the locking projection 412 of the rear ratchet 410 in modes other than vibration mode. (C) is a cross-sectional view AA of Figure 22(A), showing the positional relationship between the locking projection 373 of the clutch hub 370 and the locking projection 412 of the rear ratchet 410 in vibration mode. This is an explanatory diagram of the engagement between the two. [Figure 23] (A) to (E) are diagrams illustrating the main components of the work implement 1 in clutch mode with the minimum tightening torque set, viewed from different viewpoints, with some parts cut out. [Figure 24] (A) to (E) are diagrams illustrating the main components of the work implement 1 in clutch mode with the maximum tightening torque set, viewed from different viewpoints, with some parts cut out. [Figure 25] (A) to (E) are diagrams illustrating the main components of the work machine 1 set to drill mode, viewed from different viewpoints, with some parts cut out. [Figure 26] (A) to (E) are diagrams illustrating the main components of the work machine 1 set to vibration mode, viewed from different viewpoints, with some parts cut out. [Figure 27] A perspective view of the transmission / output component 4, seen from the rear. [Figure 28] Left side view of transmission / output component 4. [Figure 29] Rear view of the transmission / output component 4. [Figure 30] A cross-sectional view of the back of the transmission / output component 4, cut at the engagement portion between the shift arm 71 and the slide ring gear 57. [Figure 31] A perspective view of the upper part of work implement 1, equipped with a sub-handle 600, as seen from the front. [Figure 32] A perspective view of the upper part of implement 1, equipped with a sub-handle 600, seen from the rear. [Figure 33] Front view of implement 1 with sub-handle 600 attached. [Figure 34] A cross-sectional view of work implement 1 with a sub-handle 600 attached. [Figure 35] A cross-sectional view of the sub-handle 600. [Figure 36] Exploded perspective view of the Subhandle 600. [Figure 37] An exploded perspective view of the sub-handle 600, seen from a different viewpoint than Figure 36. [Figure 38] Diagram illustrating the opening and closing range of the mounting portion 601 of the sub-handle 600. [Figure 39] A diagram showing that the sub-handle 600 can rotate within a predetermined angular range when stored. [Modes for carrying out the invention]

[0017] This embodiment relates to a work implement 1, which is a rotary hammer drill. Figures 3 and 4 define the mutually orthogonal front-rear and up-down directions of the work implement 1. In addition, the left-right direction, which is perpendicular to the front-rear and up-down directions, is defined relative to a worker facing forward.

[0018] The front-rear direction is parallel to the axial direction of the motor shaft 31. The front side corresponds to one side in the axial direction. The rear side corresponds to the other side in the axial direction. The up-down direction is the direction that connects the motor housing 11 and the battery pack mounting section 13 perpendicular to the front-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 with a left and right two-part structure. The housing 10 has a motor housing section 11, a handle section 12, and a battery pack mounting section 13.

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

[0021] The handle portion 12 extends downward from the lower part of the motor housing portion 11. The work implement 1 is equipped with a trigger switch 17 at the upper end of the handle portion 12 that can switch the motor 30 on and off. The work implement 1 is equipped with a forward / reverse switch 19 at the boundary between the motor housing portion 11 and the handle portion 12 that can switch the motor 30 on and off.

[0022] The battery pack mounting section 13 is connected to the lower end of the handle section 12. The battery pack mounting section 13 is detachably equipped with a battery pack 25, which is the power source for the work machine 1. As shown in Figure 4, the work machine 1 includes a control board section 23 inside the battery pack mounting section 13. The control board section 23 is equipped with a microcontroller that controls the driving of the motor 30, an inverter circuit for supplying current to the motor 30, and the like.

[0023] As shown in Figure 4, the work machine 1 includes a motor 30, a fan 35, and a sensor board 37 within a motor housing 11. The motor 30 is, for example, an inner rotor type brushless motor and is driven by the power of the battery pack 25. The motor 30 has a motor shaft 31 which serves as the output shaft. The fan 35 is located behind the main body of the motor 30 (the part of the motor 30 excluding the motor shaft 31) and rotates integrally with the motor shaft 31, generating cooling air to cool the motor 30 and other components. The sensor board 37 is located 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, which outputs a signal corresponding to the rotational position of the motor 30.

[0024] (Configuration of transmission / output component 4) Figures 5 to 20 show the configuration of the transmission / output component 4 (transmission / output unit) of the work machine 1, that is, the configuration of the part in front of the motor 30.

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

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

[0027] The bearing retaining portion 41 is located in the rear center of the motor spacer 40. As shown in Figure 4, the bearing retaining portion 41 holds the ball bearing 33 (bearing) that supports the front 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 the 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 secure the motor spacer 40 and the rear case 60 to the gear case 140. The two upper screws 44 correspond to the first fixing part, and the two lower screws 44 correspond to the second fixing part. The screws 44 extend in the front-rear direction. The screw collars 45 shown in Figures 6 and 7 are made of metal, for example, and are members through which the two upper screws 44 pass.

[0029] The transmission / output component 4 includes a rear case 60 as a cylindrical case for the 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 threaded boss portions 62 as insertion portions, a guide projection 63, a guide hole 64, a spring retaining hole 65, a flange portion 66, and two through holes 67.

[0031] The cylindrical portion 61 is a cylindrical part coaxial with the motor shaft 31. The screw boss portions 62 are provided on the lower left and lower right sides of the cylindrical portion 61, respectively, so as to protrude radially outward. The through hole 67 penetrates the screw boss portion 62 in the front-to-back direction. The through hole 67 is the portion through which the two lower screws 44 shown in Figures 6 and 7 pass.

[0032] The guide projection 63 functions as a rotation guide for the shift arm 71. The guide hole 64 is a through-hole (groove-shaped hole) through which the shift arm 71 passes, and serves as a guide for the forward and backward movement of the lower part of the shift arm 71. The spring retaining hole 65 opens on the front surface of the flange portion 66 and is a non-through hole that holds the rear end of the stopper spring 117 shown in Figures 5 to 7. The flange portion 66 widens radially outward from the front end of the cylindrical portion 61.

[0033] The left grease cover 68 and the right grease cover 69 shown in Figures 6 and 7 are made of resin, for example, and are attached to the left and right sides of the cylindrical part 61 so as to cover the left and right guide holes 64, and each functions as a space to collect 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 metal, for example.

[0035] As shown in Figures 9(A) to (G), the final ring gear 90 has six outer peripheral protrusions 91 (projections), a cylindrical portion 92, a flange portion 93, a gear portion 94, six frontal protrusions 95, and six frontal recesses 96.

[0036] The cylindrical portion 92 is a cylindrical part 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 protrusions 91 are arranged at equal angular intervals in the circumferential direction and each protrudes radially outward from the front outer peripheral surface of the cylindrical portion 92. The outer peripheral protrusions 91 are provided spanning the front 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 circumferential surface of the cylindrical portion 92.

[0037] The front protrusions 95 and front recesses 96 are provided on the front surface of the flange portion 93. The six front recesses 96 are arranged at equal angular intervals in the circumferential direction. The front protrusions 95 are located between adjacent front recesses 96. The rear end of the clutch pin 131, described later, is pressed against the front recesses 96.

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

[0039] As shown in Figures 10(A) to (H), the stopper block 120 has a base portion 121, a spring holding portion 122, a locking projection 123, and a wide projection 124.

[0040] The base portion 121 is a planar portion (plate-shaped portion) that follows the inner circumferential surface of the gear case 140. The spring holding portion 122 is a recess provided on the back of the base portion 121 and holds the front end of the stopper spring 117 shown in Figures 5 to 7. The base portion 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 projection 123 is provided on one surface of the base 121 that faces the outer circumferential surface of the final ring gear 90. The locking projection 123 is a projection that engages with the outer circumferential projection 91 of the final ring gear 90 when it is in the locking position described later, thereby preventing the final ring gear 90 from rotating.

[0042] The wide protrusion 124 is located behind the locking protrusion 123. It is wider in the circumferential direction 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 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 of the rear cylindrical portion 141 to the rear of the front cylindrical portion 150 and extends radially inward to the front cylindrical portion 150. The 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 holds a pin sleeve 161 (for example, made of metal) as shown in Figures 6 and 7.

[0046] The three anti-rotation portions 144 are arranged at equal angular intervals in the circumferential direction, and each branches into two and protrudes forward from the front end of the front cylindrical portion 150. The anti-rotation portions 144 sandwich the anti-rotation projections 285 of the ratchet cam ring 280 (described later) from both sides in the circumferential direction, making the ratchet cam ring 280 unable to rotate.

[0047] The three through holes 145 penetrate the front wall portion 142 in the front-to-back direction on the radially inner side of the front cylindrical portion 150. The through holes 145 are the portions through which the screws 133 shown in Figures 5 to 7 pass, and correspond to the mounting portion on the transmission housing side. The spring washers 135 shown in Figures 6 to 7 are, for example, made of metal, and are interposed between the head of the screw 133 and the periphery of the through hole 145 to suppress loosening of the screw 133. The central through hole 146 is the portion through which the spindle 470 passes. The four through holes 147 are the portions through which the screws 27 shown in Figure 1, i.e., the screws 27 for fixing the gear case 140 to the motor housing portion 11 from the front, pass.

[0048] The anti-rotation protrusions 148 and 149 are projections that engage (fit) with the anti-rotation recesses 218 and 219 of the rear stopper cam ring 210, described later, to prevent the rear stopper cam ring 210 from rotating. The front cylindrical part 150 is a cylindrical part that is coaxial with the motor shaft 31 and has a smaller diameter than the rear cylindrical part 141. The four screw holes 151 are the parts into which the screws 44 shown in Figures 6 and 7 are screwed.

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

[0050] The three stopper insertion holes 153 each penetrate the front wall portion 142 in the front-to-back direction and communicate with the stopper insertion groove 152. The stopper block 120 can protrude forward from the front wall portion 142 by passing through each of the stopper insertion holes 153.

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

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

[0053] The needle bearing 53 shown in Figures 6 and 7 is interposed between the inner circumferential surface of the first planetary gear 51 and the pin protruding from the rear of 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 accordance with the forward and backward movement of the end of the shift arm 71 that occurs as the shift arm 71 rotates.

[0055] When the sliding ring gear 57 is in the forward position, it meshes with the second planetary gear 81. At this time, the sliding ring gear 57 is fixed in a non-rotatable position by the shift dog 75 (for example, made of metal), and the transmission mechanism 50 has a high reduction ratio with three stages of reduction.

[0056] When the slide ring gear 57 is in the rearward position, 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 due to the two-stage reduction.

[0057] The spline hub 105 shown in Figures 5 to 7 is made of metal, for example, and engages with the inner circumference of the final carrier 101 and the outer circumference 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 metal, for example.

[0058] The roller 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 to the final carrier 101. When attempting to rotate the chuck 500, the roller 103 is clamped and fixed between the outer circumference of the spline hub 105 and the inner circumference of the lock ring 110. The components are positioned such that the roller 103 is not fixed when rotation is transmitted from the final carrier 101 to the spindle 470 and chuck 500.

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

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

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

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

[0063] The flat portion 211 is a planar surface perpendicular to the front-rear direction, 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. The outer peripheral inclined portion 212 has one end connected to the flat portion 211 and is an inclined surface that slopes from the flat portion 211 so that it moves towards the rear as you move clockwise when viewed from the front. The outer peripheral flat portion 213 is a planar surface perpendicular to the front-rear direction that 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 constitute a recess or hole.

[0064] The inner circumferential inclined portion 214 is provided on the radially inner portion of the front surface of the rear stopper cam ring 210. The inner circumferential inclined portion 214 is located approximately 180° apart from the outer circumferential inclined portion 212 in the circumferential direction. The inner circumferential inclined portion 214 has one end connected to the flat portion 211 and is an inclined surface that slopes from the flat portion 211 so that it moves towards the rear as you proceed clockwise when viewed from the front. The inner circumferential flat portion 215 is a planar portion perpendicular to the front-rear direction that 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 constitute a recess or hole.

[0065] The anti-rotation recesses 218 and 219 engage (fit) with the anti-rotation protrusions 148 and 149 of the gear case 140, thereby preventing the rear stopper cam ring 210 from rotating 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 Figures 13(A) to (G), the front stopper cam ring 230 has an outer circumference projection 232, an inner circumference projection 234, and two locking projections 235.

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

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

[0071] The two locking projections 235 protrude forward from the radially outer portion of the front stopper cam ring 230 at positions approximately 180° apart in the circumferential direction. The locking projections 235 are flat or curved plate-shaped portions that are substantially perpendicular to the radial direction. The locking projections 235 engage (fit) with the locking recesses 302 of the clutch dial 300, which will be described later. As a result, the front stopper cam ring 230 rotates 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 Figures 14(A) to (E), the nut 260 has a threaded portion 261, six spring locking holes 262, and three notches 263.

[0074] The threaded portion 261 is provided on the outer circumferential 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 (for example, made of metal) shown in Figures 5 to 7. The three notches 263 are arranged at equal angular intervals in the circumferential direction and each allows the screw 133 shown in Figures 5 to 7 to pass through.

[0075] The thrust plate 165 shown in Figures 6 and 7 is made of metal, for example, and is biased rearward relative to the nut 260 by the clutch spring 250, pressing the front end of the clutch pin 131 rearward and pressing the rear end of the clutch pin 131 against the front surface of the final ring gear 90. The clutch pin 131 is made of metal, for example, and extends in the front-rear direction through a pin sleeve 161 held in the through hole 143 of the gear case 140.

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

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

[0078] The outer peripheral projection 282 protrudes 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 substantially perpendicular to the radial direction.

[0079] The inner circumferential projection 284 protrudes forward from the radially inner portion of the ratchet cam ring 280. The inner circumferential projection 284 is a flat or curved plate-like portion that is substantially 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 of the bifurcated anti-rotation portion 144 of the gear case 140. This prevents the ratchet cam ring 280 from rotating relative to the gear case 140. The back surface of the anti-rotation protrusions 285 contacts the front surface of the outer protrusion 372 of the clutch hub 370, which will be described later, and is pressed forward.

[0081] The three small protrusions 288 each project radially inward at a predetermined angle in the circumferential direction from the anti-rotation projection 285. The small protrusions 288 contact the outer circumferential surface of the threaded boss portion 345 of the front case 340 (described later) where the circumferential position of the anti-rotation projection 285 coincides with the circumferential position of the outer projection 372 of the clutch hub 370, and thus serve to position the circumferential direction.

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

[0083] The transmission / output component 4 includes a clutch dial 300 as a switching operation unit. 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 circumference recess 304, an outer circumference 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 and a cross-section perpendicular to the front-rear direction that is approximately circular, with a diameter that decreases towards 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 circumferential surface of the cylindrical portion 306. The threaded portion 301 is screwed into the threaded portion 261 of the aforementioned nut 260. The clutch dial 300 is sandwiched between the gear case 140 and the front case 340 (described later) in the front-rear direction, and its position in the front-rear direction is fixed. Therefore, the nut 260 moves in the front-rear direction in conjunction with the rotation of the clutch dial 300.

[0087] The two locking recesses 302 are located approximately 180° apart from each other in the circumferential direction and are each formed as a notch by partially cutting out the lower end of the threaded portion 301. The locking recesses 302 engage with the locking projection 235 of the front stopper cam ring 230, causing the front stopper cam ring 230 to rotate together with the clutch dial 300.

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

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

[0090] The leaf spring mounting section 308 is the part to which the leaf spring 331 (for example, made of metal) shown in Figures 6 and 7 is attached.

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

[0092] As shown in Figures 17(A) to (E), the front case 340 has a large diameter cylindrical portion 341, a small diameter cylindrical portion 342, a connecting surface portion 343, three notches 344, three screw boss portions 345, 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 section 341 is a cylindrical section coaxial with the motor shaft 31. The small-diameter cylindrical section 342 is a cylindrical section coaxial with the motor shaft 31. The small-diameter cylindrical section 342 has a smaller diameter than the large-diameter cylindrical section 341 and is located behind the large-diameter cylindrical section 341. The small-diameter cylindrical section 342 contains a ratchet spring 360, a rear ratchet 410, a front ratchet 440, a ball bearing 461, etc. The connecting surface section 343 is a wall section perpendicular to the front-rear direction that connects the rear end of the large-diameter cylindrical section 341 and the front end of the small-diameter cylindrical section 342.

[0094] The three notches 344 are arranged at equal angular intervals in the circumferential direction and each passes through the outer projection 372 of the clutch hub 370, which will be described later. The three threaded bosses 345 are arranged at equal angular intervals in the circumferential direction and each is provided so as to project radially outward from the outer circumferential surface of the small diameter cylindrical portion 342. The three threaded holes 347 are non-through holes that open on the back surface of the threaded bosses 345, and the screws 133 shown in Figures 5 to 7 are screwed into each of them. The threaded bosses 345 and threaded holes 347 correspond to the mounting portions on the output housing side.

[0095] The three screw holes 346 are non-through holes opening on the front surface of the connecting surface 343, and each is screwed with a screw 489 as shown in Figures 5 to 7. The three screw holes 346 are located in the same positions as the three screw holes 347 in the circumferential direction. The bearing holder 348 holds the ball bearing 335 (bearing) as shown in Figures 5 to 7. The ball bearing 335 is made of metal, for example, and rotatably supports the rear of the spindle 470.

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

[0097] The two retaining projections 350 are positioned approximately 180° apart from each other in the circumferential direction and protrude radially outward from the left and right sides of the outer 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 projection 349. The retaining projections 350 extend from the anti-rotation projection 349 on both sides in the circumferential direction. The retaining projections 350 prevent the sub-handle 600, described later, from coming out (detaching) forward from the front case 340.

[0098] The locking recess 351 is a groove into which the leaf spring 331 fits, and there are recesses corresponding to each stage of the set tightening torque in clutch mode, as well as recesses corresponding to drill mode and vibration mode. When the leaf spring 331 fits into the locking recess 351, the rotational position of the clutch dial 300 is determined, and the clutch dial 300 is locked in the rotational direction, holding it in place to prevent accidental rotation.

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

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

[0101] As shown in Figures 18(A) to (E), the clutch hub 370 has an annular portion 371, three outward 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 each protrudes 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 vibrating part. The rear ratchet 410 is made of metal, for example.

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

[0105] The thrust bearing 391 and bearing washer 395 shown in Figures 6 and 7 are made of metal, for example, and are interposed between the back surface of the rear ratchet 410 and the surface of the front case 340 opposite it, and are subjected to loads in the front-rear direction. The thrust bearing 391 and bearing washer 395 reduce friction when the tip tool 20 is used in pressure against a mating material, thereby suppressing power loss.

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

[0107] As shown in Figures 20(A) to (F), the front ratchet 440 is ring-shaped and has a recessed portion 441 on its back surface. The recessed portion 441 is a vibration-generating shape, and by contacting the recessed portion 411 (vibration-generating shape) of the rear ratchet 410 and rotating relative to it, it outputs vibration to the spindle 470.

[0108] The spring 431 shown in Figures 5 to 7 is made of metal, for example, and biases the front ratchet 440 forward relative to the rear ratchet 410. As a result, when the tip tool 20 is not pressed against the workpiece, the rear ratchet 410 and the front ratchet 440 are not in contact, and vibration is suppressed. The ratchet washer 435 is made of metal, for example, and avoids contact between the front ratchet 440 and the spring 431, thereby reducing friction.

[0109] The ball bearing 461 shown in Figures 5 to 7 is made of metal, for example, and rotatably supports the front ratchet 440 and the intermediate 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 comprises a spindle 470 and a chuck 500. Both the spindle 470 and the chuck 500 are 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 tip 20 shown in Figure 3 and rotates together with the spindle 470.

[0111] The threaded portion on the rear inner surface of the chuck 500 is screwed into the threaded portion on the front outer surface 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-hand thread 495 (for example, made of metal). The spindle 470 and the chuck 500 are firmly fixed to each other, forming a substantially integrated tool holder.

[0112] The bearing cover 485 shown in Figures 5 to 7 is made of metal, for example, and is fixed to the front case 340 by screws 489 that pass through its own through-holes 487 and are screwed into the screw holes 346 of the front case 340.

[0113] The O-ring 481 shown in Figures 5 to 7 is made of an elastic material such as rubber and is placed between the inner circumferential surface of the bearing cover 485 and the outer circumferential surface of the spindle 470. The O-ring 481 slides along the inner circumferential surface of the bearing cover 485, reducing the impact when rotation stops (braking). The O-ring 481 also has the function of preventing oil leakage.

[0114] The retaining ring 483 shown in Figures 5 to 7 is, for example, made of metal and is provided on the inner circumferential surface of the small-diameter cylindrical portion 342 of the front case 340, and functions as a retainer for the ball bearing 461.

[0115] (Decomposability of transmission / output component 4) Figure 21 is a right-side cross-sectional view showing the transmission / output component 4 separated into the transmission unit 5, output switching unit 6, and output unit 7.

[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 components (transmission mechanism 50, etc.) held or supported therein.

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

[0118] The output unit 7 includes the front case 340 and the components held or supported therein, namely the spindle 470, the chuck 500, the ball bearings 335 and 461, etc.

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

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

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

[0122] (Clutch mode, Drill mode, Vibration mode) The work implement 1 has clutch mode, drill mode, and vibration mode, and one of these 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 cut off when the set tightening torque (predetermined torque) is exceeded, i.e., a mode in which the clutch mechanism is active. The set tightening torque can be adjusted in multiple stages, for example, 22 stages, by operating the clutch dial 300.

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

[0125] The clutch mechanism stops the rotation of the final ring gear 90 until the set tightening torque is reached, and then allows the rotation of the final ring gear 90 once the set tightening torque is exceeded. The clutch mechanism includes a nut 260, a clutch spring 250, a thrust plate 165, and a clutch pin 131.

[0126] When a load (torque) is applied to the tip tool 20 while the motor 30 is in operation, the unfixed final ring gear 90 attempts 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. As a result, the final ring gear 90 becomes unable to rotate, and torque transmission by the transmission mechanism 50 becomes effective.

[0127] On the other hand, if the torque applied to the tip tool 20 increases and exceeds the set tightening torque, that is, if a load (torque) greater than the force exerted by the clutch pin 131 to push the final ring gear 90 backward and stop its rotation is applied to the final ring gear 90, the final ring gear 90 will rotate, and the clutch pin 131 will move over the front protrusion 95 of the final ring gear 90. This is the clutch operation, and 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 compression amount of the clutch spring 250. Turning the clutch dial 300 moves the nut 260 back and forth, changing the compression amount of the clutch spring 250.

[0129] In the states shown in Figures 23(A) to (E), the nut 260 is in its furthest forward position, and the compression of the clutch spring 250 is at its minimum (the set tightening torque is at its minimum). If the nut 260 is rotated clockwise when viewed from the front from this state, the nut 260 will retract, and the compression of the clutch spring 250 will increase. In the states shown in Figures 24(A) to (E), the nut 260 is in its furthest backward position, and the compression of the clutch spring 250 is at its maximum (the set tightening torque is at its maximum).

[0130] (Configuration for switching to drill mode) The drill mode is a mode in which the final ring gear 90 is rendered inoperable without the clutch mechanism, and it is the mode that can produce the maximum tightening torque as the work machine 1.

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

[0132] The configuration for switching to 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 locked position (forward position) and an unlocked position (retracted position), and when in the locked position, it prevents the final ring gear 90 from rotating. The front end of the stopper block 120 protrudes forward of the final ring gear 90. The stopper spring 117 is made of metal, for example, and biases the stopper block 120 forward, i.e., toward the locked position.

[0134] The clutch dial 300 is a switching operation unit that can switch the position of the stopper block 120 between a locked position and an unlocked position. The clutch dial 300 is located on the front side of the final ring gear 90. The clutch dial 300 is rotatable around the 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 parts that restrict the 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 and release by the rear stopper cam ring 210 and the front stopper cam ring 230 can be switched 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 in front of the stopper block 120, and its rear surface is in contact with the stopper block 120. The rear stopper cam ring 210 is in contact with the stopper block 120 on the outside of the final ring gear 90 in the radial direction of the final ring gear 90. The rear stopper cam ring 210 is located in front of the final ring gear 90. The rear stopper cam ring 210 is biased 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 protrusions 148, 149 of the gear case 140 and the anti-rotation recesses 218, 219 of the rear stopper cam ring 210.

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

[0138] The rear stopper cam ring 210 has an outer circumferential inclined portion 212 and an outer circumferential flat portion 213 as recesses, and an inner circumferential inclined portion 214 and an inner circumferential flat portion 215 as recesses. The front stopper cam ring 230 has an outer circumferential projection 232 and an inner circumferential projection 234 as convex portions. In the process of the front stopper cam ring 230 reaching a predetermined rotation position (the process of the clutch dial 300 reaching the rotation position in drill mode), the outer circumferential projection 232 and the inner circumferential projection 234 descend the outer circumferential inclined portion 212 and the inner circumferential inclined portion 214, and the rear stopper cam ring 210 moves forward. The inclination of the outer circumferential inclined portion 212 and the inner circumferential inclined portion 214 should be steeper than the inclination of the threaded portion 301 of the clutch dial 300.

[0139] Figures 24(A)-(E) and 25(A)-(E) show the process of switching from clutch mode to drill mode, where the outer peripheral projection 232 of the front stopper cam ring 230 descends the outer peripheral inclined portion 212 of the rear stopper cam ring 210, the rear stopper cam ring 210 moves forward due to the biasing force of the stopper spring 117, and the stopper block 120 moves to the locked position (forward position). In drill mode, the locking projection 123 of the stopper block 120 in the locked position engages (contacts in the rotational direction) with the outer peripheral projection 91 of the final ring gear 90, preventing the final ring gear 90 from rotating. The locking projection 123 of the stopper block 120 in the unlocked position does not engage with the outer peripheral projection 91 of the final ring gear 90, allowing the final ring gear 90 to rotate.

[0140] When the clutch dial 300 is within a predetermined rotation range corresponding to the aforementioned clutch modes (a rotation position between the states shown in Figures 23(A) to (E) and Figures 24(A) to (E)), the outer peripheral projection 232 and inner peripheral projection 234 of the front stopper cam ring 230 are in contact with the flat portion 211 of the rear stopper cam ring 210, the rear stopper cam ring 210 does not move forward, and the stopper block 120 does not move to the locked position.

[0141] (Configuration for switching to vibration mode) The vibration mode is a mode in which vibration in the forward and backward direction is applied to the spindle 470 in drill mode.

[0142] From the state shown in Figures 25(A) to (E), i.e., the drill mode, rotating the clutch dial 300 clockwise when viewed from the front to the rotation position corresponding to the vibration mode results in the state shown in Figures 26(A) to (E), i.e., the vibration mode.

[0143] The configuration for switching to drill mode includes a ratchet cam ring 280, a ratchet spring 360, a clutch hub 370, a rear ratchet 410, and a front ratchet 440.

[0144] The rear ratchet 410 and the front ratchet 440 are vibrating parts that output the driving force of the motor 30 as vibration to the spindle 470. The front ratchet 440 is driven (rotates) by the driving force of the motor 30. The clutch dial 300 switches the vibration on state and vibration off state of the rear ratchet 410 and the front ratchet 440.

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

[0146] The outer circumferential projection 282 and inner circumferential projection 284 of the ratchet cam ring 280 shown in Figures 15(A) to (E) and (G), and the inner circumferential recess 304 and outer circumferential hole 305 of the clutch dial 300 shown in Figures 16(A) to (C) and (E), are guides 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 the rotational position corresponding to the vibration mode.

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

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

[0149] The clutch hub 370 does not restrict the movement of the rear ratchet 410 in the vibration-off position, but restricts the movement of the rear ratchet 410 in the vibration-on position. Vibration occurs when the front ratchet 440 is driven by the motor 30's driving force against the rear ratchet 410, whose movement is restricted.

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

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

[0152] Figures 25(A)-(E) and 26(A)-(E) show that, during the transition from drill mode to vibration mode, the ratchet cam ring 280 and clutch hub 370 move forward due to the biasing force of the ratchet spring 360, and the front-rear position of the locking projection 373 of the clutch hub 370 and the locking projection 412 of the rear ratchet 410 coincides. During this process, the outer peripheral projection 232 and inner peripheral projection 234 of the front stopper cam ring 230 move on the outer peripheral flat portion 213 and inner peripheral flat portion 215 of the rear stopper cam ring 210, and the rotation restriction of the final ring gear 90 by the 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 rotation position between the states shown in Figures 23(A) to (E) and Figures 25(A) to (E)), the outer peripheral projection 282 and inner peripheral projection 284 of the ratchet cam ring 280 are in contact with the flat portion (a flat portion perpendicular to the front-rear direction) of the clutch dial 300, and the ratchet cam ring 280 and clutch hub 370 do not move forward (they do not move to the vibration-on position).

[0154] (How to route the shift arm 71) As mentioned 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 overall rigidity of the transmission housing, suppressing deformation, for example, when the clutch mechanism is operated.

[0155] On the other hand, in a configuration where the shift arm 71 extends radially through the outside of the screw 44 to the guide hole 64 of the rear case 60, the motor housing 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 Figures 27 to 30, in the work machine 1, the shift arm 71 extends radially through the inside of the screw 44 to the guide hole 64 of the rear case 60.

[0157] With the motor spacer 40, rear case 60, and gear case 140 fixed together 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 that extend in the front-to-back direction along the outside of the rear case 60 that are inserted into a screw collar 45, which is a separate cylindrical portion from the rear case 60. That is, the two upper screws 44 each pass through the screw insertion hole 43 of the motor spacer 40 and the screw collar 45, and are screwed into the screw hole 151 of the gear case 140. The screw collar 45 is used to prevent the motor spacer 40 from bending or breaking due to overtightening of the two upper screws 44. The shift arm 71 passes through the gap between the outer surface of the screw collar 45 and the outer 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 screw holes 151 of the gear case 140. The screw boss portion 62 having the through holes 67 is part of the rear case 60 (integrated 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 area through which the shift arm 71 passes, so there are no issues such as increasing the size.

[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 implement 1 with the sub-handle 600 attached. Figures 35 to 38 show the sub-handle 600 as a standalone unit. The front case 340 is the handle mounting portion of the work implement 1. Note that the sub-handle 600 is not limited to a mounting configuration that extends to the left from the work implement 1 as shown in Figure 31, etc., but can also be mounted in a configuration that extends to the right from the work implement 1.

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

[0162] The mounting portion 601 is annular in shape with a gap 614 in a part of its circumferential direction, and engages with the front case 340 of the work machine 1. The mounting 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 located on the upper part of the annular portion 615 and is provided on one side of the gap 614 (the left side in Figure 35) in the longitudinal direction of the gap 614 (hereinafter referred to as the "gap length direction"), and extends in the gap length direction.

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

[0165] The second cylindrical portion 613 is located above the annular portion 615 and on one side of the gap 614 (the right side in Figure 35) in the direction of the gap length, and extends in the direction of the gap length. The central axes of the first cylindrical portion 612 and the second cylindrical portion 613 are parallel to the direction of the gap length.

[0166] The second cylindrical portion 613 has a shaft insertion portion 627 and an enlarged diameter portion 628. The shaft insertion portion 627 is through which the shaft portion 611 of the first shaft portion 602 passes. The enlarged diameter portion 628 is located on the other side of the shaft insertion portion 627 (right side in Figure 35) in the gap length direction, and has a larger diameter than the shaft insertion portion 627, through which the shaft portion 611 of the first shaft portion 602 passes and into which the end of the second shaft portion 603 is inserted. The pin layer through hole 606 faces the interior of the enlarged 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 spaced approximately 180° apart in the circumferential direction of the mounting portion 601. The two first anti-rotation recesses 616 face each other with the center of the mounting portion 601 in between. The ten second anti-rotation recesses 617 are spaced five at a time at equal angular intervals between the two first anti-rotation recesses 616 in the circumferential direction of the mounting portion 601. The length of the first anti-rotation recesses 616 in the circumferential direction of the mounting portion 601 is longer than that of 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 secure the depth gauge.

[0169] The first shaft portion 602 and the second shaft portion 603 constitute an adjustment mechanism that can adjust the length of the gap 614 within a predetermined range, including a length longer than the natural length. The natural length is the length of the gap 614 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 direction of the gap length and is mounted on the mount portion 601 on one side of the gap 614 (the left side in Figure 35) in the direction of the gap length so as to be immovable in the direction of the gap length. The first shaft portion 602 passes through the gap 614 and protrudes from the mount portion 601 to the other side in the direction of the gap length.

[0171] The second shaft portion 603 extends in the direction of the gap length and is mounted on the mount portion 601 so as not to move in the longitudinal direction on the other side of the gap 614 (right side in Figure 35) in the direction of the gap length. The second shaft portion 603 protrudes from the mount portion 601 to the other side in the longitudinal direction.

[0172] The first shaft portion 602 and the second shaft portion 603 are engaged with each other so as to be movable relative to each other in the direction of the gap length, 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 direction of the gap length.

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

[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 direction of the gap length, and is larger than the shaft portion 611 when viewed from the direction of the gap length and is non-circular, for example, hexagonal. The head portion 610 fits into the head retaining portion 624 of the mount portion 601, so that the first shaft portion 602 cannot rotate relative to the mount portion 601 and so that the first shaft portion 602 cannot come out of the mount portion 601 on the other side in the direction of the gap length (right side in Figure 35). In addition, a retaining ring 608 provided on the inner circumferential surface of the first cylindrical portion 612 adjacent to the head retaining portion 624 prevents the first shaft portion 602 from coming out of the mount portion 601 on one side in the direction of the gap length (left side in Figure 35).

[0175] The shaft portion 611 extends from the head portion 610 to the other side in the direction of the gap length, passes through the shaft portion insertion portions 626 and 627 of the mounting portion 601, and reaches the inside of the second shaft portion 603. A male threaded portion 622 is provided on the outer circumferential surface of the tip 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 enlarged diameter portion 628 of the second cylindrical portion 613 of the mounting portion 601. Both the small-diameter portion 619 and the enlarged diameter portion 628 have a circular cross-section. The small-diameter portion 619 has a pin insertion groove 620 and an O-ring insertion groove 621. The pin insertion groove 620 and the O-ring insertion groove 621 are grooves that encircle the outer circumference of the small-diameter portion 619. The pin insertion groove 620 is located on one side (the left side in Figure 35) of the O-ring insertion groove 621 in the gap length direction.

[0178] The pin 607, inserted into the pin layer through hole 606, extends into the pin insertion groove 620. The pin layer through hole 606 is located at the same position as the pin insertion groove 620 in the gap length direction. The pin 607 is inserted into the pin layer through hole 606 and extends into the interior of the pin insertion groove 620, making the second shaft portion 603 immobile 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 is fitted into the O-ring fitting groove 621. The O-ring 609 generates frictional resistance against the rotation of the second shaft portion 603 relative to the second cylindrical portion 613, preventing the second shaft portion 603 from rotating easily.

[0180] The second shaft portion 603 has a nut portion 623 that constitutes the female thread portion. The nut portion 623 is screwed 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 it may be integrated with them. In the example in 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 rotated, the entire second shaft portion 603 rotates integrally with the mount portion 601 and the first shaft portion 602. In conjunction with this, the screw engagement between the male threaded portion 622 of the first shaft portion 602 and the nut 623 of the second shaft portion 603 causes the second shaft portion 603 to move relative to the first shaft portion 602 in the direction of the gap length. At this time, the engagement between the second shaft portion 603 and the second cylindrical portion 613 of the mount portion 601 via the pin 607 causes the second cylindrical portion 613 to move relative to the first cylindrical portion 612 in the direction of the gap length. This adjusts the length of the gap 614.

[0182] In the state shown in Figures 38(B) and (E), i.e., when the gap 614 is at its natural length, rotating the grip portion 604 to the left moves the second shaft portion 603 to the other side in the gap length direction (the right side in Figure 38), thereby adjusting the length of the gap 614 to be longer than its natural length. Figures 38(C) and (F) show the state where the gap 614 is at its maximum length, i.e., when the mount portion 601 is fully open. The length of the screw engagement between the male threaded 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 gap 614 length is within a predetermined length that does not damage the mount portion 601.

[0183] As shown in Figures 38(B) and (E), that is, when the gap 614 is at its natural length, rotating the grip portion 604 to the right moves the second shaft portion 603 and the second cylindrical portion 613 of the mount portion 601 relative to one side in the direction of the gap length (the left side in Figure 35), thereby adjusting the length of the gap 614 to be shorter than its natural length. Figures 38(A) and (D) show the state where the length of the gap 614 is at its minimum, that is, the state where the mount portion 601 is most closed. By adjusting the length of the gap 614 to be shorter than its natural length, the mount portion 601 can be tightened against the front case 340, and the sub-handle 600 can be fixed to the front case 340.

[0184] By making the gap 614 wider than its natural length, the front case 340 of the work implement 1 can pass inside the mounting portion 601. The retaining projection 350 of the front case 340 is large enough that it cannot be inserted inside the mounting portion 601 when the gap 614 is at its natural length. The retaining projection 350 prevents the mounting portion 601 from coming out forward from the front case 340 when the gap 614 is at or below its natural length.

[0185] (Easy storage structure for the 600mm sub-handle) 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, then fit the mounting part 601 into the front case 340 from the front. After that, rotate 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 mounting angle can be selected from multiple positions. Of the two first anti-rotation recesses 616 and ten second anti-rotation recesses 617 of the mounting portion 601, two corresponding to the mounting 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 mounting portion 601 is longer than the circumferential length of the anti-rotation projection 349 of the front case 340. The circumferential length of the second anti-rotation recess 617 of the mounting portion 601 is approximately equal to the circumferential length of the anti-rotation projection 349 of the front case 340.

[0188] When the second anti-rotation recess 617 of the mounting portion 601 and the anti-rotation projection 349 of the front case 340 engage with each other, their circumferential lengths are approximately equal, allowing the sub-handle 600 to be mounted on the front case 340 with little to no rattle. The second anti-rotation recess 617 of the mounting portion 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 mounting portion 601 and the anti-rotation projection 349 of the front case 340 engage with each other, the circumferential length of the first anti-rotation recess 616 is longer than the circumferential length of the anti-rotation projection 349, allowing the sub-handle 600 to rotate within a predetermined angular 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] Figures 39(A) to (C) show that the sub-handle 600 can rotate within a predetermined angular range when stored.

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

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

[0193] Even when the first anti-rotation recess 616 of the mounting portion 601 and the anti-rotation projection 349 of the front case 340 engage in a concave-concave-concave configuration, by making the gap 614 of the mounting portion 601 shorter than a predetermined length, the frictional force caused by the mounting portion 601 tightening against the front case 340 prevents the sub-handle 600 from rotating relative to the front case 340.

[0194] This embodiment provides the following effects and benefits.

[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 positioned 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 from the output unit 7 towards the rear. Specifically, when the screw 133 is removed and the gear case 140 is removed from the front case 340 (the transmission unit 5 is removed from the output unit 7), the output switching unit 6 can be removed from the output unit 7 towards the rear. Therefore, even if the spindle 470 and chuck 500 cannot be released from their fixed positions, the components of the output switching unit 6, namely the clutch dial 300, nut 260, clutch spring 250, etc., can be replaced, resulting in good repairability.

[0196] For comparison, we consider a configuration in which the gear case 140 is extended forward to hold the ball bearings 335 and 461, and a retaining ring prevents the clutch dial 300 from coming out forward relative to the gear case 140 (hereinafter referred to as "comparative configuration 1"). In comparative configuration 1, the retaining ring cannot be accessed without removing the chuck 500 from the spindle 470, and the clutch dial 300, etc., cannot be removed either forward or backward. Therefore, in comparative configuration 1, if the clutch dial 300, etc., is damaged and needs to be replaced, it is necessary to remove the chuck 500 from the spindle 470 using a special jig, or to replace the entire transmission / output component 4, which increases the time and cost required for repair. This embodiment suitably solves such problems.

[0197] (2) The transmission unit 5 and the output unit 7 can be used as a module in common across multiple models, making them highly convenient.

[0198] (3) The work machine 1 includes a transmission mechanism 50 including a final ring gear 90, a stopper block 120 that prevents the final ring gear 90 from rotating when it is in the locked position, and a stopper spring 117 that biases 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 toward the locked position comes into contact with the rear end of the outer circumference protrusion 91 of the final ring gear 90 and is unable to reach the locked position, if the final ring gear 90 rotates thereafter, the outer circumference protrusion 91 will move from in front of the protrusion 123, and the stopper block 120 will automatically move toward the locked position. Thus, it is possible to suppress the problem of being unable to prevent the final ring gear 90 from rotating, that is, the problem of being unable to switch to drill mode.

[0199] (4) The work machine 1 can switch the position of the stopper block 120 between a locked position and an 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 not due to screw engagement using the rotation of the clutch dial 300. Therefore, compared to a configuration in which the stopper pin is pushed toward the final ring gear 90 by a nut 260 that moves back and forth in conjunction with the rotation of the clutch dial 300, the problem of not being able to rotate the clutch dial 300 to the drill mode rotation position is suppressed, and it is easy 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 located behind the clutch dial 300. Therefore, compared to the case in which the stopper spring 117 and the stopper block 120 are located inside the clutch dial 300, an increase in the diameter of the clutch dial 300 can be suppressed, and deterioration of the operability of rotating the clutch dial 300 can be suppressed.

[0201] (6) The rear stopper cam ring 210 and the front stopper cam ring 230 function as restrictors that restrict the movement of the stopper block 120 from the unlocked position to the locked position against the biasing force of the stopper spring 117 when the clutch dial 300 is within the rotation range of the clutch mode. The rear stopper cam ring 210 and the front stopper cam ring 230 also 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 between the rotation position of the drill mode and the rotation position of the clutch mode. As a result, the forward and backward movement of the stopper block 120 (movement between the unlocked position and the locked position) can be suitably achieved, limited to when the clutch dial 300 rotates between the rotation position of the drill mode and the rotation position of the clutch mode, without relying on screw engagement between the clutch dial 300 and the nut 260.

[0202] (7) When the clutch dial 300 rotates between the rotation position of drill mode and the rotation position of clutch mode, the outer circumferential projection 232 and inner circumferential projection 234 of the front stopper cam ring 230 move along the outer circumferential inclined portion 212 and inner circumferential inclined portion 214 of the rear stopper cam ring 210. By making the inclination angle of the outer circumferential inclined portion 212 and inner circumferential inclined portion 214 steeper than the inclination of the threaded portion 301 of the clutch dial 300, the stopper block 120 can be moved back and forth in conjunction with the rotation of the clutch dial 300, compared to the case where the stopper block 120 is moved by the threaded engagement between the clutch dial 300 and the nut 260. This reduces the amount of operation of the clutch dial 300 required to switch between clutch mode and drill mode, making it easier to use. Furthermore, since the outer circumferential inclined portion 212 and the inner circumferential inclined portion 214 form a recess, the outer circumferential projection 232 and the inner circumferential projection 234 of the front stopper cam ring 230 can easily move in and out of the recess. Therefore, sticking when switching between clutch mode and drill mode is suppressed, resulting in improved usability.

[0203] (8) The rear stopper cam ring 210 is located in front 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 drill mode (stopper block 120, stopper spring 117, rear stopper cam ring 210, front stopper cam ring 230) is distributed in front of and behind the final ring gear 90. Therefore, unlike the case in which the configuration for switching to drill mode is biased to one side of the final ring gear 90, it is easier to balance the radial size of the gear case 140 and the clutch dial 300, resulting in better layout efficiency.

[0204] (9) When the clutch hub 370 of the work machine 1 is in the vibration-on position, the clutch hub 370 restricts the movement of the rear ratchet 410. The front ratchet 440 is driven by the motor 30 against the restricted movement of the rear ratchet 410, generating vibration. When the clutch dial 300 is in the rotation position corresponding to the vibration mode, the outer peripheral projection 282 and inner peripheral projection 284 of the ratchet cam ring 280 enter the outer peripheral hole 305 and inner peripheral recess 304 of the clutch dial 300 along their respective inclined portions 286 and 287, and the ratchet cam ring 280 and clutch hub 370 move from the vibration-off position to the vibration-on position due to the biasing force of the ratchet spring 360. Therefore, compared to a configuration in which the clutch hub 370 is pushed forward by a nut 260 that moves back and forth in conjunction with the rotation of the clutch dial 300, the amount of operation of the clutch dial 300 required to switch between vibration and non-vibration can be reduced, making it easier to use.

[0205] (10) Because the outer circumferential projection 282 and inner circumferential projection 284 of the ratchet cam ring 280 have inclined portions 286 and 287, the outer circumferential projection 282 and inner circumferential projection 284 can move smoothly in and out of the outer circumferential hole 305 and inner circumferential recess 304 of the clutch dial 300, which suppresses sticking when switching between drill mode and vibration mode, making it easy to use.

[0206] (11) The ratchet cam ring 280 and the clutch dial 300 function as restrictors that restrict the movement of the clutch hub 370 from the vibration-off position to the vibration-on position against the biasing force of the ratchet spring 360 when the clutch dial 300 is within the rotation range of the clutch mode and drill mode. The ratchet cam ring 280 and the clutch dial 300 also constitute a cam mechanism that moves the clutch hub 370 between the vibration-off position and the vibration-on position in conjunction with the rotation of the clutch dial 300 between the rotation position of the vibration mode and the rotation position of the drill mode. Therefore, the forward and backward movement of the clutch hub 370 (movement between the vibration-off position and the vibration-on position) can be suitably achieved, limited to when the clutch dial 300 rotates between the rotation position of the vibration mode and the rotation position of the drill mode, without relying on screw engagement between the clutch dial 300 and the nut 260.

[0207] (12) As shown in Figures 22(B) and (C), the circumferential sides of the locking projection 373 of the clutch hub 370 and the locking projection 412 of the rear ratchet 410 are provided with inclined portions 374 and 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 of the inclined portions 374 and 413 applies a forward force to the clutch hub 370, making it difficult for it to move to the vibration-off position. Therefore, the clutch hub 370 is prevented from unintentionally moving to the vibration-off position due to vibration or the like.

[0208] (13) The motor spacer 40, rear case 60, and gear case 140 are fixed together with four screws 44, forming a highly rigid transmission housing that suppresses deformation when the clutch mechanism is operated. On the other hand, there is a gap between the outer surface of the rear case 60 and the two upper screws 44, and the shift arm 71 extends through this gap to the guide hole 64 of the rear case 60. Therefore, compared to a configuration in which the shift arm 71 extends radially through the outside of the screws 44 to the guide hole 64 of the rear case 60, it is possible to suppress the enlargement of the motor housing 11 that covers the outside of the shift arm 71, thereby suppressing the enlargement of the product.

[0209] (14) The two upper screws 44 have portions that extend in the front-to-back direction outside the rear case 60 that are inserted into screw collars 45, which are cylindrical portions separate from the rear case 60. This prevents the motor spacer 40 from bending or being damaged due to overtightening of the two upper screws 44.

[0210] (15) The front case 340 has a retaining projection 350 for the sub-handle 600, which prevents the sub-handle 600 from coming out forward due to vibrations during work, resulting in improved workability.

[0211] (16) The sub-handle 600 is an annular shape having a gap 614 in a part of its circumference and includes a mounting portion 601 that engages with the front case 340 of the work machine 1, and is configured to be adjustable in a predetermined range including a length longer than the natural length of the gap 614. Therefore, even if the gap 614 of the front case 340 is at its natural length and interferes with, for example, the retaining projection 350 of the front case 340, making it difficult to attach or detach, the gap 614 can be easily attached or detached by adjusting its length to be longer than the natural length.

[0212] (17) The first shaft portion 602 and the second shaft portion 603 are screw-engaged with each other, and the length of the gap 614 can be adjusted by rotating 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 into 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. The pin 607 allows the rotation of the second shaft portion 603, so that it is not prevented from rotating the second shaft portion 603 to adjust the length of the gap 614.

[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, thereby preventing the second shaft portion 603 from rotating easily and improving workability.

[0215] (20) The length of the screw engagement between the male threaded 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 does not damage the mount portion 601. Therefore, damage to the mount portion 601 due to excessive widening of the gap 614 can be suppressed regardless of the user's operation, making it easy to use.

[0216] (21) The mounting portion 601 has a first anti-rotation recess 616 which has a long circumferential length and a second anti-rotation recess 617 which has a short circumferential length. When the second anti-rotation recess 617 and the anti-rotation projection 349 of the front case 340 engage in a concave-concave If the angle when stored cannot be changed from the angle shown in Figure 39(C), the guard portion 625 of the grip portion 604 will interfere with the battery pack 25, the battery pack mounting portion 13, etc., making it difficult to store. However, this embodiment can suitably solve such problems.

[0217] (22) Even when the first anti-rotation recess 616 of the mount portion 601 and the anti-rotation projection 349 of the front case 340 engage in a concave-concave-concave engagement, by making the gap 614 of the mount portion 601 shorter than a predetermined length, the frictional force caused by the mount portion 601 tightening the front case 340 can prevent the sub-handle 600 from rotating relative to the front case 340. Therefore, rattling of the sub-handle 600 in the stored state can be suppressed as needed. Furthermore, even when the first anti-rotation recess 616 of the mount portion 601 is configured to be used when the work implement 1 is in use, rattling during operation can also be suppressed.

[0218] Although the present invention has been described above using embodiments as examples, the present invention is not limited to these embodiments. Various modifications are possible to each of the matters specifically described in the embodiments within the scope of the claims.

[0219] The concave and convex structures illustrated in the embodiments may have their concave and convex relationships reversed as appropriate. For example, the rear stopper cam ring 210 may have a convex portion, and the front stopper cam ring 230 may have a concave portion that engages with the convex portion. Similarly, the ratchet cam ring 280 may have a concave portion, and the clutch dial 300 may have a convex portion that engages with the concave portion.

[0220] The specific numbers exemplified in the embodiment, such as the number of outer circumference protrusions 91 on the final ring gear 90, the number of stopper blocks 120, the number of screws 44 and 133, the number of stages for the set tightening torque, the number of possible mounting angles for the sub-handle 600 on the work machine 1, and the number of first anti-rotation recesses 616 and second anti-rotation recesses 617, do not limit the scope of the invention in any way and can be arbitrarily changed to suit the required specifications. [Explanation of symbols]

[0221] 1...Work implement, 4...Transmission / output component, 5...Transmission unit, 6...Output switching unit, 7...Output unit, 10...Housing, 11...Motor housing, 12...Handle unit, 13...Battery pack mounting unit, 15...Tail cover, 17...Trigger switch, 19...Forward / reverse switch, 20...Cutting tool, 21...Shift knob, 23...Control board unit, 25...Battery pack, 27...Screw, 30...Motor, 31...Motor shaft, 33...Ball bearing, 35...Fan, 37...Sensor board, 40...Motor spacer, 41...Bearing holder, 42...Gear unit, 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 section, 60...Rear case, 61...Cylindrical section, 62...Screw boss section, 63...Guide projection, 64...Guide hole, 65...Spring retention hole, 66...Flange section, 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 circumference projection, 92...Cylindrical section, 93...Flange section, 94...Gear section, 95...Front projection, 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 part, 123...locking projection (projection), 124...wide projection, 131...clutch pin, 133...screw, 135...spring washer, 140...gear case, 141...rear cylindrical part, 142...front wall part, 143...through hole, 144...anti-rotation part, 145...through hole, 146...central through hole, 147...through hole, 148... 149…Protruding part of the anti-rotation mechanism, 150…Front cylindrical part, 151…Screw hole, 152…Stopper insertion groove, stopper insertion hole, 161…Pin sleeve, 165…Thrust plate, 210…Rear stopper cam ring, 211…Flat part, 212…Outer circumference inclined part, 213…Outer circumference flat part, 214…Inner circumference inclined part, 215…Inner circumference flat part, 218…Anti-rotation recess, 219…Anti-rotation recess, 230…Front stopper cam ring, 232…Outer circumference projection, 234…Inner circumference projection, 235…Locking projection, 250…Clutch spring, 260…Nut, 261…Screw part,262...Spring locking hole, 263...Notch, 280...Ratchet cam ring, 282...Outer circumference projection, 284...Inner circumference projection, 285...Anti-rotation protrusion, 286...Inclined section, 287...Inclined section, 288...Small projection, 300...Clutch dial, 301...Screw section, 302...Locking recess, 304...Inner circumference recess, 305...Outer circumference hole, 306...Cylindrical section, 307...Front wall section, 308...Leaf spring mounting section, 331...Leaf spring, 335...Ball bearing, 340...Front case, 34 1...Large diameter cylinder section, 342...Small diameter cylinder section, 343...Connecting surface section, 344...Notch section, 345...Threaded boss section, 346...Threaded hole, 347...Threaded hole, 348...Bearing holding section, 349...Anti-rotation projection (rotation restricting section), 350...Anti-detachment projection, 351...Locking recess, 360...Ratchet spring, 370...Clutch hub, 371...Annular section, 372...Outer projection, 373...Locking projection, 374...Inclined section, 391...Thrust bearing, 395...Bearing washer, 410...Rear ratchet, 411...Rear bumps (vibration) 412...Vibration-generating shape part, 413...Inclined part, 431...Spring, 435...Ratchet washer, 440...Front ratchet, 441...Concave and concave part (vibration-generating shape part), 461...Ball bearing, 470...Spindle, 481...O-ring, 483...Retaining ring, 485...Bearing cover, 487...Through hole, 489...Screw, 495...Left-hand thread, 500...Chuck, 600...Sub-handle, 601...Mounting part, 602...First shaft part, 603...Second shaft part, 604...Grip part, 6 05...Knob bolt, 606...Pin layer through hole, 607...Pin, 608...Retaining ring, 609...O-ring, 610...Head, 611...Shaft, 612...First cylindrical part, 613...Second cylindrical part, 614...Gap, 615...Annular part, 616...First anti-rotation recess, 617...Second anti-rotation recess, 618...Large diameter part, 619...Small diameter part, 620...Pin insertion groove, 621...O-ring insertion groove, 622...Male thread part, 623...Nut part, 624...Head holding part, 625...Flange part, 626...Shaft insertion part, 627...Shaft insertion part, 628...Enlarged diameter part.

Claims

1. Motor and, A reduction mechanism having a ring gear for reducing the rotation of the motor, A stopper portion that is movable between a locked position and an unlocked position, and which prevents the ring gear from rotating when it is in the locked position, A biasing means for biasing the stopper portion toward the locking position, A clutch dial operated by the operator to adjust the set tightening torque, The device includes a clutch mechanism that stops the rotation of the ring gear until the set tightening torque is reached, and allows the rotation of the ring gear once the set tightening torque is exceeded, A work machine that allows selection of at least one of the following modes: a clutch mode in which the clutch mechanism allows the ring gear to rotate when the set tightening torque is exceeded, and a drill mode in which the ring gear is prevented from rotating by the clutch mechanism, The clutch dial is configured and includes a switching operation unit that can switch the position of the stopper portion between the locked position and the unlocked position. When the clutch mode is selected, the stopper portion is in the non-locking position and does not engage with the ring gear in the rotational direction. When the switching operation unit is operated to a predetermined position corresponding to the drill mode from the state in which the clutch mode is selected, the stopper portion moves from the unlocked position to the locked position due to the biasing of the biasing means, the stopper portion engages with the ring gear in the rotational direction, and the system switches to the drill mode. A work machine characterized by the following features.

2. In the axial direction of the motor, the switching operation unit is located on one side of the ring gear. The biasing means biases the stopper portion toward one side in the axial direction. The work machine according to feature 1.

3. The end of the stopper portion on one side in the axial direction protrudes further in the axial direction than the ring gear. The work machine according to feature 2.

4. The system includes a restricting portion that restricts the movement of the stopper portion from the unlocked position to the locked position against the biasing force of the biasing means, The restriction by the restricting unit can be switched by operating the switching operation unit. The work machine according to feature 2.

5. The switching operation unit is the clutch dial which is rotatable around the extension of the motor's axis, The regulating part includes a cam mechanism that moves the stopper part between the unlocked position and the locked position in conjunction with the rotation of the clutch dial. The work machine according to feature 4.

6. The aforementioned regulatory body, A first cam is located on one side of the stopper portion in the axial direction and is in contact with the stopper portion, and is biased toward one side in the axial direction by the biasing means via the stopper portion, thereby restricting its rotation. It has a second cam located on one side of the first cam in the axial direction and rotating together with the clutch dial, When the second cam reaches a predetermined rotational position, the first cam moves to one side in the axial direction, and the restriction by the restricting part is released. The work machine according to feature 5.

7. One of the first and second cams has a recess or hole and the other has a protrusion, When the second cam reaches the predetermined rotational position, the protrusion enters the recess or hole, the first cam moves to one side in the axial direction, and the restriction by the restricting part is released. The work machine according to feature 6.

8. At least one of the first and second cams has an inclined portion that facilitates the movement of the convex portion into the concave portion or hole portion. The work machine according to feature 7.

9. The first cam contacts the stopper portion on the outside of the ring gear in the radial direction of the ring gear. The work machine according to feature 6 or 7.

10. The first cam is located on one side of the ring gear in the axial direction. The work machine according to feature 6 or 7.

11. The tip tool holder and, It comprises a clutch mechanism that interrupts the transmission of rotation from the reduction mechanism to the tip tool holder at a predetermined torque, The clutch dial is capable of switching the predetermined torque within a predetermined rotation range. When the clutch dial is within the predetermined rotation range, the second cam does not come to the predetermined rotation position. The work machine according to feature 6 or 7.

12. The stopper portion has a projection that engages with the ring gear when in the locked position, located radially inward from the contact portion with the first cam. The work machine according to feature 9.

13. Motor and, A reduction mechanism having a planetary gear mechanism including planetary gears and ring gears, which reduces the rotation of the motor, A spindle, which is rotationally driven by the motor via the reduction mechanism and rotates integrally with the chuck that holds the tip tool, A clutch dial operated by the operator to adjust the set tightening torque, The device includes a clutch mechanism that stops the rotation of the ring gear until the set tightening torque is reached, and allows the rotation of the ring gear once the set tightening torque is exceeded, A work machine that allows selection of at least one of the following modes: a clutch mode in which the clutch mechanism allows the ring gear to rotate when the set tightening torque is exceeded, and a drill mode in which the ring gear is prevented from rotating by the clutch mechanism, A stopper portion is movable between a locked position and an unlocked position, and when in the locked position, it engages with the ring gear in the rotational direction to prevent the ring gear from rotating, while when in the unlocked position, it does not engage with the ring gear in the rotational direction and allows the ring gear to rotate. A switching operation unit that allows the operator to switch the position of the stopper between the locked position and the unlocked position, A biasing means for biasing the stopper portion toward the locking position, A restricting unit capable of restricting the movement of the stopper portion from the unlocked position to the locked position against the biasing force of the biasing means, comprising a restricting unit that, by operation of the switching operation unit, switches between restricting the movement of the stopper portion from the unlocked position to the locked position, or releasing the restriction on the movement of the stopper portion from the unlocked position to the locked position, When the clutch mode is selected, the switching operation unit is operated to a predetermined position corresponding to the drill mode, the restriction by the restricting unit on the movement of the stopper unit from the unlocked position to the locked position is released, the stopper unit moves from the unlocked position to the locked position due to the biasing force of the biasing means, the stopper unit engages with the ring gear in the rotational direction, and the system switches to the drill mode. A work machine characterized by the following features.

14. The switching operation unit is configured as the clutch dial, The work machine according to feature 13.

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