Work machine

Abstract

The invention provides a work machine with good repairability. The work machine (1) is provided with an output switching unit (6) that switches the output (presence or absence of torque or vibration) of the output unit (7) and is disposed so as to be sandwiched 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) to the rear side. Specifically, when the screw 133 is removed and the gearbox 140 is removed from the front shell 340 (the transmission part 5 is removed from the output part 7), the output switching part 6 can be removed from the output part 7 to the rear side.

Description

Technical Field

[0001] The invention relates to a working machine. Background Art

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

[0003] A working machine such as a screwdriver and an electric drill includes: a motor; a spindle; a transmission mechanism that transmits the rotation of the motor to the spindle; a chuck that is screwed to the spindle; a reduction ratio switching mechanism that switches the reduction ratio of the transmission mechanism; and a clutch mechanism that cuts off the rotation transmission from the transmission mechanism to the spindle at a specified torque.

[0004] The reduction ratio switching mechanism has a shift knob operated by a user, and a shift arm for advancing and retracting a slide ring gear of a transmission mechanism in conjunction with the operation of the shift knob. The clutch mechanism has a clutch dial for the user to change a specified torque. A screwdriver drill with a vibration function such as that in Patent Document 2 is also called a vibration screwdriver drill, and the presence or absence of vibration can be switched by operating the clutch dial.

[0005] Prior art literature

[0006] Patent Literature

[0007] Patent Document 1: Japanese Patent Application Publication No. 2014-018914

[0008] Patent Document 2: Japanese Patent Application Publication No. 2015-191735

[0009] Patent Document 3: Japanese Patent Application Publication No. 2017-80853 Summary of the invention

[0010] Problems to be solved by the invention

[0011] In working machines such as screwdrivers and electric drills, the chuck and the spindle are fixed with high torque, and a special fixture is required to release the fixation. That is, without a special fixture, the chuck and the spindle become a substantially integrated top tool holding part. Therefore, it is difficult to replace parts that cannot be removed without releasing the fixation between the chuck and the spindle. In previous working machines, there are many parts that are difficult to replace and the repairability is poor. The first problem recognized by the inventor is to provide a working machine with good repairability.

[0012] A work machine such as a screwdriver electric drill is put into an electric drill mode with maximum torque by fixing the ring gear of the transmission mechanism so as to be non-rotatable. As a structure for putting into the electric drill mode, there is a structure in which a stop pin is pushed toward the ring gear side by a nut that rotates together with the clutch dial and moves axially. Here, depending on the rotation position of the ring gear, there is sometimes a part of the ring gear on the extension of the stop pin. In the said structure, when the stop pin abuts against the said part, the clutch dial no longer rotates and cannot be transferred to the electric drill mode, which is inconvenient to use. The second problem recognized by the inventor is to provide a work machine that can suppress the undesirable situation that the ring gear cannot be made non-rotatable.

[0013] In a working machine such as a screwdriver and an electric drill, when a transmission mechanism is housed in a plurality of shells separated in the front-to-back direction, the rigidity of the shells is increased by fixing the plurality of shells in the front-to-back direction using fixing parts such as screws, thereby suppressing deformation. Here, in a structure in which a speed change arm passes through the outer side of the fixing part in the radial direction of the shell, the product is enlarged in the radial direction. The third problem recognized by the inventor is to provide a working machine capable of suppressing enlargement.

[0014] In a work machine such as a vibration screwdriver, if the clutch dial operation required to switch the vibration is large, the switching of the vibration is time-consuming and the workability is poor. The fourth problem recognized by the inventor is to provide a work machine that can reduce the time required to switch the vibration.

[0015] As a structure of a handle that can be detachably mounted on a work machine, there is known a structure that is mounted on the work machine in a manner that closes the gap of an annular mounting portion having a gap (opening) in a part of the circumference. In this structure, when the maximum length of the gap of the mounting portion is the natural length, it is sometimes difficult to mount and remove the handle. The fifth problem recognized by the inventor is to provide a handle that can be easily mounted and removed from a work machine, and a work machine including a handle that can be easily mounted and removed.

[0016] If the handle cannot be moved when installed on the work machine, it is inconvenient to be unable to fine-tune the installation state of the handle. The sixth problem recognized by the inventor is to provide a handle that can fine-tune the installation state relative to the work machine, and a work machine including a handle whose installation state can be fine-tuned.

[0017] An object of the present invention is to provide a working machine that solves at least the first of the above-mentioned problems.

[0018] Technical means of solving problems

[0019] A certain embodiment of the present invention is a working machine. The working machine includes: a motor; an output part having a top tool holding part and a bearing part supporting the top tool holding part, and located on one side of the motor in the axial direction of the motor; a transmission part that transmits the driving force of the motor to the top tool holding part, which is detachably assembled to the output part from the other side in the axial direction and is located on one side of the motor in the axial direction; and an output switching part that switches the output of the output part and is clamped by the output part and the transmission part. If the transmission part is removed from the output part, the output switching part can be removed from the output part to the other side in the axial direction.

[0020] The present invention may be expressed as "electric working machine", "electric tool", "electric equipment" or the like, and machines expressed in this way are also effective as embodiments of the present invention.

[0021] Effects of the Invention

[0022] According to the present invention, it is possible to provide a working machine that solves at least the first problem among the above-mentioned problems. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] [ Figure 1 ] is a stereoscopic view of the working machine 1 according to the embodiment of the present invention as viewed from the front side.

[0024] [ Figure 2 ] is a stereoscopic view of the working machine 1 as viewed from the rear side.

[0025] [ Figure 3 ] is a right side view of the working machine 1.

[0026] [ Figure 4 ] is a right side sectional view of the working machine 1.

[0027] [ Figure 5 ] is an enlarged right side sectional view showing the structure of the transmission / output structure 4 of the working machine 1.

[0028] [ Figure 6 ] is an exploded stereoscopic view of the transmission / output structure 4, and is a stereoscopic view obtained by observing from the front side.

[0029] [ Figure 7 ] is an exploded stereoscopic view of the transmission / output structure 4, and is a stereoscopic view obtained by observing from the rear side.

[0030] [ Figure 8 (A) is correct Figure 5 to Figure 7(B) is a perspective view of the rear case 60 as seen from the front. (C) is a front view of the rear case 60. (D) is a perspective view of the rear case 60 as seen from the rear. Figure 8 (C) is the AA cross-section. (E) is Figure 8 (C) is a BB cross-sectional view. (F) is a rear view of the rear case 60. (G) is a right side view of the rear case 60.

[0031] [ Fig. 9 (A) is correct Figure 5 to Figure 7 (A) is a perspective view of the final ring gear 90 as seen from the front. (B) is a perspective view of the final ring gear 90 as seen from the rear. (C) is a front view of the final ring gear 90. (D) is Fig. 9 (C) is the AA cross-section. (E) is Fig. 9 (C) is a BB cross-sectional view. (F) is a rear view of the final ring gear 90. (G) is a right side view of the final ring gear 90.

[0032] [ Fig.10 ](A)~(D) are correct Figure 5 to Figure 7 The stopper block 120 shown in FIG. 1 is a three-dimensional view obtained by observing the stopper block 120 from different viewpoints. (E) is a front view of the stopper block 120. (F) is Fig.10 (E) is a cross-sectional view taken along the line AA. (G) is a rear view of the stopper block 120. (G) is a right side view of the stopper block 120.

[0033] [ Fig.11 (A) Yes Figure 5 to Figure 7 (B) is a perspective view of the gear box 140. (C) is a perspective view of the gear box 140. Fig.11 (B) is a cross-sectional view taken along the line AA. (D) is a rear view of the gear box 140. (E) is a right side view of the gear box 140.

[0034] [ Fig.12 (A) is correct Figure 5 to Figure 7 (A) is a perspective view of the rear stop cam ring 210 as seen from the front. (B) is a perspective view of the rear stop cam ring 210 as seen from the rear. (C) is a front view of the rear stop cam ring 210. (D) is a perspective view of the rear stop cam ring 210 as seen from the rear. Fig.12 (C) is the AA cross-section. (E) is Fig.12 (C) is a BB cross-sectional view. (F) is a back view of the rear stopper cam ring 210. (G) is a right side view of the rear stopper cam ring 210.

[0035] [ Fig.13 (A) is correct Figure 5 to Figure 7(A) is a perspective view of the front stop cam ring 230 as seen from the front side. (B) is a perspective view of the front stop cam ring 230 as seen from the rear side. (C) is a front view of the front stop cam ring 230. (D) is Fig.13 (C) is the AA cross-section. (E) is Fig.13 (C) is a BB cross-sectional view. (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.

[0036] [ Fig.14 (A) Yes Figure 5 to Figure 7 (B) is a perspective view of the nut 260. (C) is a perspective view of the nut 260. Fig.14 (B) is a cross-sectional view taken along the line AA. (D) is a rear view of the nut 260. (E) is a right side view of the nut 260.

[0037] [ Fig.15 (A) is correct Figure 5 to Figure 7 (B) is a perspective view of the ratchet cam ring 280 as seen from the front. (C) is a front view of the ratchet cam ring 280. (D) is a perspective view of the ratchet cam ring 280 as seen from the rear. Fig.15 (C) is the AA cross-section. (E) is Fig.15 (C) is a BB cross-sectional view. (F) is a rear view of the ratchet cam ring 280. (G) is a right side view of the ratchet cam ring 280.

[0038] [ Fig.16 (A) is correct Figure 5 to Figure 7 (B) is a perspective view of the clutch dial 300 as seen from the front. (C) is a front view of the clutch dial 300. (D) is a perspective view of the clutch dial 300 as seen from the rear. Fig.16 (C) is a cross-sectional view taken along the line AA. (E) is a rear view of the clutch dial 300. (F) is a right side view of the clutch dial 300.

[0039] [ Fig.17 (A) Yes Figure 5 to Figure 7 (B) is a perspective view of the front shell 340. (C) is a perspective view of the front shell 340. Fig.17 (B) is a cross-sectional view taken along the line AA. (D) is a rear view of the front housing 340. (E) is a right side view of the front housing 340.

[0040] [ Fig.18 (A) Yes Figure 5 to Figure 7 (B) is a perspective view of the clutch hub 370. (C) is a perspective view of the clutch hub 370. Fig.18(B) is a cross-sectional view taken along the line AA. (D) is a rear view of the clutch hub 370. (E) is a right side view of the clutch hub 370.

[0041] [ Fig.19 (A) is correct Figure 5 to Figure 7 (B) is a perspective view of the rear ratchet 410 as seen from the front. (C) is a front view of the rear ratchet 410. (D) is a perspective view of the rear ratchet 410 as seen from the rear. Fig.19 (C) is a cross-sectional view taken along the line AA. (E) is a back view of the rear ratchet 410. (F) is a right side view of the rear ratchet 410.

[0042] [ Fig. 20 (A) is correct Figure 5 to Figure 7 (B) is a stereoscopic view of the front ratchet 440 as shown in FIG. 4 from the front side. (C) is a front view of the front ratchet 440. (D) is a left side view of the front ratchet 440. (E) is a back view of the front ratchet 440. (F) is a Fig. 20 (E) AA cross-section.

[0043] [ Fig.21 ] is a right side cross-sectional view showing the state where the transmission / output structure unit 4 is separated into the transmission unit 5, the output switching unit 6, and the output unit 7.

[0044] [ Fig. 22 ] (A) is a view of the clutch hub 370 and the rear ratchet 410 viewed from the front. (B) is Fig. 22 (A) is a cross-sectional view taken along the line AA, and is a diagram showing the positional relationship between the locking protrusion 373 of the clutch hub 370 and the locking protrusion 412 of the rear ratchet 410 outside the vibration mode. (C) is Fig. 22 (A) is a cross-sectional view taken along the line AA, and is a diagram 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 the vibration mode.

[0045] [ Fig.23 ](A) to (E) are main part structure explanatory diagrams of the working machine 1 when the working machine 1 is set to the clutch mode and the tightening torque is set to the minimum, respectively, observed from different viewpoints, and are structure explanatory diagrams with a portion cut away.

[0046] [ Fig.24 ](A) to (E) are main structure explanatory diagrams of the working machine 1 when the clutch mode is set and the tightening torque is set to the maximum, respectively, observed from different viewpoints, and are structure explanatory diagrams with a portion cut away.

[0047] [ Fig.25 ](A) to (E) are diagrams for explaining the structure of the main parts of the working machine 1 set to the electric drill mode, observed from different viewpoints, and are diagrams for explaining the structure with a portion cut away.

[0048] [ Fig.26 ](A) to (E) are main structure explanatory diagrams of the working machine 1 set to the vibration mode, observed from different viewpoints, and are structure explanatory diagrams with a portion cut away.

[0049] [ Fig. 27 ] is a stereoscopic view of the transmission / output structure 4 observed from the rear.

[0050] [ Fig.28 ] is a left side view of the transmission / output structure 4.

[0051] [ Fig.29 ] is a back view of the transmission / output structure 4.

[0052] [ Fig.30 ] is a rear cross-sectional view of the transmission / output structure portion 4, and is a cross-sectional view obtained by cutting the engaging portion between the speed change arm 71 and the sliding ring gear 57.

[0053] [ Fig.31 ] is a stereoscopic view of the upper portion of the working machine 1 equipped with the sub-handle 600, viewed from the front.

[0054] [ Fig.32 ] is a stereoscopic view of the upper portion of the working machine 1 equipped with the auxiliary handle 600, viewed from the rear.

[0055] [ Fig.33 ] is a front view of the working machine 1 equipped with a sub-handle 600.

[0056] [ Fig.34 ] is a front cross-sectional view of the working machine 1 equipped with a sub-handle 600.

[0057] [ Fig.35 ] is a front cross-sectional view of the sub-handle 600.

[0058] [ Fig.36 ] is an exploded stereoscopic view of the sub-handle 600.

[0059] [ Fig.37 ] is to connect the sub-handle 600 to Fig.36 Exploded stereograms obtained by observing from different viewpoints.

[0060] [ Fig.38 ] is an illustration of the openable and closable range of the mounting portion 601 of the sub-handle 600.

[0061] [ Fig.39 ] is a diagram showing that the sub-handle 600 can rotate within a prescribed angle range in the stored state. DETAILED DESCRIPTION

[0062] This embodiment relates to a working machine 1. The working machine 1 is a vibration screwdriver electric drill. Figure 3 and Figure 4 , define the front-rear direction and the up-down direction that are orthogonal to each other of the working machine 1. In addition, the left-right direction that is perpendicular to the front-rear direction and the up-down direction is defined with the operator facing forward as a reference.

[0063] The front-to-back direction is a direction parallel to the axial direction of the motor shaft 31. The front side corresponds to one side in the axial direction. The rear side corresponds to the other side in the axial direction. The up-down direction is a direction connecting the motor housing portion 11 and the battery assembly mounting portion 13 perpendicularly to the front-to-back direction.

[0064] like Figure 1 to Figure 4 As shown, the working machine 1 includes a housing 10. The housing 10 is, for example, a resin molded body having a structure divided into two parts, the left and right parts. The housing 10 includes a motor housing portion 11, a handle portion 12, and a battery pack mounting portion 13.

[0065] The motor housing 11 is a cylindrical portion whose central axis is parallel to the front-rear direction. The working machine 1 includes a tail cover 15 covering the rear opening of the motor housing 11. The working machine 1 includes a speed change knob 21 on the upper part of the motor housing 11. The speed change knob 21 is a speed reduction ratio switching operation portion, which is used to Figure 5 to Figure 7 The shift arm 71 appears in the middle and rotates to move the sliding ring gear 57 described later forward and backward, thereby Figure 5 The speed change arm 71 is made of metal, for example, and corresponds to a speed reduction ratio switching unit.

[0066] The handle portion 12 extends downward from the lower portion of the motor housing portion 11. The working machine 1 includes a trigger switch 17 capable of switching the driving and stopping of the motor 30 at the upper end portion of the handle portion 12. The working machine 1 includes a forward and reverse switching switch 19 capable of switching the forward and reverse rotation of the motor 30 at the boundary portion between the motor housing portion 11 and the handle portion 12.

[0067] The battery pack installation part 13 is connected to the lower end of the handle part 12. The battery pack installation part 13 is installed with a battery pack 25 as a power source of the working machine 1 in a detachable manner. Figure 4 As shown, the working machine 1 includes a control board unit 23 in the battery pack installation unit 13. The control board unit 23 is equipped with a microcontroller for controlling the driving of the motor 30, an inverter circuit for supplying current to the motor 30, and the like.

[0068] like Figure 4As shown, the working machine 1 includes a motor 30, a fan 35, and a sensor substrate 37 in the motor housing portion 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 as an output shaft. The fan 35 is arranged at the rear of the main body of the motor 30 (the part of the motor 30 other than the motor shaft 31), rotates integrally with the motor shaft 31, and generates cooling wind to cool the motor 30, etc. The sensor substrate 37 is arranged in front of the main body of the motor 30. The sensor substrate 37 is equipped with a magnetic sensor such as a Hall integrated circuit (IC) that outputs a signal corresponding to the rotation position of the motor 30.

[0069] (Structure of the transmission / output structure 4) Figures 5 to 20 The present invention relates to the structure of the transmission / output structure portion 4 (transmission / output unit) of the working machine 1 , that is, the structure of the portion located in front of the motor 30 .

[0070] The transmission / output structure 4 includes a motor spacer 40 as a cover of a first shell.

[0071] like Figure 6 and Figure 7 As shown, the motor spacer 40 includes a bearing holding portion 41 , a gear portion 42 , and four screw insertion holes 43 .

[0072] The bearing holding portion 41 is located at the rear center of the motor spacer 40. Figure 4 As shown, the bearing holding portion 41 holds the ball bearing 33 (bearing) supporting the front portion of the motor shaft 31. The gear portion 42 is provided on the inner peripheral surface of the motor spacer 40. That is, the motor spacer 40 functions as a primary ring gear of the transmission mechanism 50.

[0073] The four screw insertion holes 43 are through holes for passing screws 44. The screws 44 are fixing parts that fix the motor spacer 40 and the rear housing 60 to the gear box 140. The two screws 44 on the upper side correspond to the first fixing part, and the two screws 44 on the lower side correspond to the second fixing part. The screws 44 extend in the front-rear direction. Figure 6-7 The screw sleeve 45 shown in the figure is made of metal, for example, and is a member through which the two upper screws 44 are passed.

[0074] The transmission / output structure 4 includes a rear case 60 as a cylindrical case of a first case. The rear case 60 is made of resin, for example.

[0075] like Figure 8 As shown in (A) to (G), the rear housing 60 has a cylindrical portion 61 , two threaded boss portions 62 as insertion portions, a guide protrusion 63 , a guide hole 64 , a spring holding hole 65 , a flange portion 66 , and two through holes 67 .

[0076] The cylindrical portion 61 is a cylindrical portion coaxial with the motor shaft 31. The threaded boss portion 62 is provided in a manner protruding radially outward at the lower left and lower right portions of the cylindrical portion 61. The through hole 67 penetrates the threaded boss portion 62 in the front-to-back direction. The through hole 67 is provided for Figure 6 and Figure 7 The portion through which the two screws 44 on the lower side appear.

[0077] The guide protrusion 63 functions as a rotation guide for the shift arm 71. The guide hole 64 is a long hole (groove-shaped hole) through which the shift arm 71 passes and passes, and serves as a guide for the lower part of the shift arm 71 to move in the forward and backward directions. The spring holding hole 65 is opened on the front surface of the flange portion 66 and holds the spring. Figure 5 to Figure 7 The flange portion 66 extends radially outward from the front end portion of the cylindrical portion 61.

[0078] Figure 6-7 The left grease cover 68 and the right grease cover 69 shown in the figure are made of resin, for example, and are installed on the left and right sides of the cylindrical portion 61 in a manner to cover the left and right guide holes 64, and function as spaces for storing lubricating oil leaking from the guide holes 64.

[0079] The transmission / output structure 4 includes a final ring gear 90. The final ring gear 90 is made of metal, for example.

[0080] like Fig. 9 As shown in (A) to (G), the final ring gear 90 has six outer peripheral side convex portions 91 (protrusions), a tubular portion 92 , a flange portion 93 , a gear portion 94 , six front surface convex portions 95 , and six front surface concave portions 96 .

[0081] The cylindrical portion 92 is a cylindrical portion coaxial with the motor shaft 31. The flange portion 93 extends radially outward from the front end of the cylindrical portion 92. Six outer peripheral side protrusions 91 are arranged at equal angles in the circumferential direction and protrude radially outward from the outer peripheral front of the cylindrical portion 92. The outer peripheral side protrusions 91 are provided across the outer peripheral front of the cylindrical portion 92 and the back of the flange portion 93. The gear portion 94 is provided on the inner peripheral surface of the cylindrical portion 92.

[0082] The front surface protrusion 95 and the front surface recess 96 are provided on the front surface of the flange portion 93. The six front surface recesses 96 are arranged at equal angles in the circumferential direction. The front surface protrusion 95 is located between adjacent front surface recesses 96. The rear end of the clutch pin 131 described later is pressed against the front surface recess 96.

[0083] The transmission / output structure 4 includes a stopper block 120 as a stopper. The stopper block 120 is made of metal, for example.

[0084] like Fig.10 As shown in (A) to (H), the stopper 120 includes a base portion 121 , a spring holding portion 122 , a locking protrusion 123 , and a wide protrusion 124 .

[0085] The base 121 is a planar portion (plate-shaped portion) along the inner peripheral surface of the gear box 140. The spring holding portion 122 is a recessed portion provided on the back side of the base 121 and holds the spring. Figure 5 to Figure 7 The front end portion of the stop spring 117 appears in the base 121. The base 121 is located between the inner circumferential surface of the gear box 140 and the outer circumferential surface of the final ring gear 90.

[0086] The locking projection 123 is provided on one of the surfaces of the base 121, which faces the outer peripheral surface of the final ring gear 90. The locking projection 123 is a protrusion that engages with the outer peripheral side projection 91 of the final ring gear 90 when in a locking position described later to prevent the final ring gear 90 from rotating.

[0087] The wide convex portion 124 is connected to the rear of the locking convex portion 123. The width in the circumferential direction is wider than that of the locking convex portion 123. The wide convex portion 124 is provided to form the spring holding hole 122.

[0088] The transmission / output structure 4 includes a gear case 140 as a second housing. The gear case 140 is made of metal, for example.

[0089] like Fig.11 As shown in (A) to (E), the gear box 140 has a rear cylindrical portion 141, a front wall portion 142, six through holes 143, three stop portions 144, three through holes 145, a central through hole 146, four through holes 147, a stop portion protrusion 148, a stop portion protrusion 149, a front cylindrical portion 150, four screw holes 151, three stop member insertion grooves 152, and three stop member insertion holes 153.

[0090] The rear cylindrical portion 141 is a cylindrical portion coaxial with the motor shaft 31 and constitutes a part of the outer shell of the working machine 1. The front wall portion 142 connects the front portion of the rear cylindrical portion 141 with the rear portion of the front cylindrical portion 150 and extends to the radial inner side of the front cylindrical portion 150. Six through holes 143 penetrate the front wall portion 142 in the front-to-back direction on the radial outer side of the front cylindrical portion 150 and respectively hold Figure 6-7 The pin sleeve 161 (eg, made of metal) appears.

[0091] The three anti-rotation parts 144 are arranged at equal angles in the circumferential direction and protrude forward in two forks from the front end of the front cylindrical part 150. The anti-rotation parts 144 clamp the anti-rotation protrusions 285 of the ratchet cam ring 280 described later from both sides in the circumferential direction, thereby preventing the ratchet cam ring 280 from rotating.

[0092] 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 provided Figure 5 to Figure 7 The portion through which the screw 133 appears corresponds to the mounting portion on the transmission portion housing side. Figure 6-7 The spring washer 135 is made of metal, for example, and is interposed between the head of the screw 133 and the periphery of the through hole 145 to prevent the screw 133 from loosening. The central through hole 146 is a portion through which the main shaft 470 passes. The four through holes 147 are for Figure 1 The screw 27 that appears in the figure is a portion through which the screw 27 for fixing the gear box 140 to the motor housing portion 11 from the front passes.

[0093] The anti-rotation protrusions 148 and 149 are protrusions that engage (fit) with the anti-rotation recesses 218 and 219 of the rear stop cam ring 210 described later to prevent the rear stop cam ring 210 from rotating. The front cylindrical portion 150 is a cylindrical portion coaxial with the motor shaft 31 and having a smaller diameter than the rear cylindrical portion 141. The four screw holes 151 are provided for Figure 6-7 The part where the screw 44 is screwed appears.

[0094] The three stopper insertion grooves 152 are grooves that are arranged at equal angles in the circumferential direction on the inner circumferential surface of the rear cylindrical portion 141 and extend in the front-rear direction. The base 121 of the stopper block 120 is embedded in each of the stopper insertion grooves 152. The stopper block 120 is guided by the stopper insertion grooves 152 and can move in the front-rear direction.

[0095] The three stopper insertion holes 153 penetrate the front wall portion 142 in the front-rear direction and communicate with the stopper insertion groove 152. The stopper block 120 can penetrate each of the stopper insertion holes 153 and protrude forward from the front wall portion 142.

[0096] The motor spacer 40 , the rear housing 60 , and the gear box 140 are assembled together by four screws 44 to form a transmission unit housing that accommodates the transmission mechanism 50 .

[0097] Here, the transmission mechanism 50 is a speed reduction mechanism including a planetary gear mechanism, and includes the gear portion 42 of the motor spacer 40, the first planetary gear 51, the first planetary carrier 55, the sliding ring gear 57, the second planetary gear 81, the second planetary carrier 85, the final planetary gear 87, the final ring gear 90, and the final planetary carrier 101. These parts constituting the transmission mechanism 50 are made of metal, for example.

[0098] Figure 6-7 The needle roller bearing 53 that appears in the middle is interposed between the inner peripheral surface of the first planetary gear 51 and the pin of the first planetary carrier 55 that protrudes toward the rear.

[0099] The sliding ring gear 57 has a groove portion 58 that engages with the end portion of the speed change arm 71. The sliding ring gear 57 moves forward and backward in accordance with the forward and backward movement of the end portion of the speed change arm 71 as the speed change arm 71 rotates.

[0100] When the sliding ring gear 57 is located in the front, it meshes with the second planetary gear 81. At this time, the sliding ring gear 57 is fixed to be non-rotatable by the shift claw 75 (for example, made of metal), and the transmission mechanism 50 has a high reduction ratio with three-stage reduction.

[0101] When the sliding ring gear 57 is located at the rear, it meshes with both the first planetary gear 51 and the second planetary gear 81. At this time, the transmission mechanism 50 has a low reduction ratio with two-stage reduction.

[0102] Figure 5 to Figure 7 The spline hub 105 is made of metal, for example, and meshes with the inner circumference of the final planetary carrier 101 and the outer circumference of the rear end of the main shaft 470 to transmit the rotation of the final planetary carrier 101 to the main shaft 470. The final planetary carrier 101 is made of metal, for example.

[0103] Figure 6-7 The roller 103 and the lock ring 110 shown in the figure are made of metal, for example, and are parts for suppressing the transmission of rotation from the main shaft 470 and the chuck 500 side to the final planetary carrier 101 side. When the chuck 500 is to be rotated, the roller 103 is clamped between the outer circumference of the spline hub 105 and the inner circumference of the lock ring 110 and fixed. The parts are in a positional relationship in which the roller 103 is not fixed when the rotation is transmitted from the final planetary carrier 101 side to the main shaft 470 and the chuck 500 side.

[0104] Figure 6-7 The hub washer 115 that appears is made of metal, for example, and is a part that is interposed between the front surface of the spline hub 105 and the back surface of the front wall portion 142 of the gear box 140 to avoid contact between the gear box 140 and the spline hub 105 and reduce friction.

[0105] The transmission / output structure portion 4 includes a rear-side stopper cam ring 210 as a first cam.

[0106] The rear stopper cam ring 210 is located in front of the stopper block 120 and contacts the front end of the stopper block 120 , and is urged forward by the stopper spring 117 via the stopper block 120 , thereby limiting rotation relative to the gear box 140 .

[0107] like Fig.12 As shown in (A) to (G), the rear stopper cam ring 210 includes a flat portion 211 , an outer peripheral inclined portion 212 , an outer peripheral flat portion 213 , an inner peripheral inclined portion 214 , an inner peripheral flat portion 215 , a rotation-stopping recess 218 , and a rotation-stopping recess 219 .

[0108] The flat portion 211 is a plane portion perpendicular to the front-to-back direction provided on the front surface of the rear stop cam ring 210. The outer circumferential side inclined portion 212 is provided on the radially outer side portion of the front surface of the rear stop cam ring 210. The outer circumferential side inclined portion 212 is an inclined surface connected to the flat portion 211 at one end and inclined with respect to the flat portion 211 in a manner that the more the right side is turned when viewed forward, the more backward. The outer circumferential side flat portion 213 is a plane portion perpendicular to the front-to-back direction extending in the circumferential direction from the other end of the outer circumferential side inclined portion 212. The outer circumferential side inclined portion 212 and the outer circumferential side flat portion 213 constitute a recess or a hole.

[0109] The inner circumferential side inclined portion 214 is provided at the radially inner portion of the front surface of the rear stop cam ring 210. The inner circumferential side inclined portion 214 is located approximately 180° away from the outer circumferential side inclined portion 212 in the circumferential direction. The inner circumferential side inclined portion 214 is an inclined surface connected to the flat portion 211 at one end and inclined relative to the flat portion 211 in a manner that the more it turns to the right when viewed forward, the more it leans toward the rear. The inner circumferential side flat portion 215 is a plane portion perpendicular to the front-rear direction and extending in the circumferential direction from the other end of the inner circumferential side inclined portion 214. The inner circumferential side inclined portion 214 and the inner circumferential side flat portion 215 constitute a recess or a hole portion.

[0110] The rotation-stopping recesses 218 and 219 are engaged (fitted) with the rotation-stopping protrusions 148 and 149 of the gear case 140 , so that the rear stopper cam ring 210 cannot rotate relative to the gear case 140 .

[0111] The transmission / output structure 4 includes a front stopper cam ring 230 as a second cam. The front stopper cam ring 230 is made of resin, for example.

[0112] The front stopper cam ring 230 is located on the front side of the rear stopper cam ring 210 , and rotates together with the clutch dial 300 .

[0113] like Fig.13 As shown in (A) to (G), the front stopper cam ring 230 has an outer peripheral protrusion 232 , an inner peripheral protrusion 234 , and two locking protrusions 235 .

[0114] The outer circumferential protrusion 232 protrudes rearward from the radially outer portion of the front stop cam ring 230. The outer circumferential protrusion 232 is a flat plate or curved plate portion substantially perpendicular to the radial direction. The radial position of the outer circumferential protrusion 232 is equal to the radial position of the outer circumferential inclined portion 212 and the outer circumferential flat portion 213 of the rear stop cam ring 210.

[0115] The inner circumferential side protrusion 234 protrudes rearward from the radial inner side portion of the front stop cam ring 230. The inner circumferential side protrusion 234 is a flat plate or curved plate portion substantially perpendicular to the radial direction. The inner circumferential side protrusion 234 is located approximately 180° away from the outer circumferential side protrusion 232 in the circumferential direction. The radial position of the inner circumferential side protrusion 234 is equal to the radial position of the inner circumferential side inclined portion 214 and the inner circumferential side flat portion 215 of the rear stop cam ring 210.

[0116] Two locking protrusions 235 protrude forward from the radially outer portion of the front stopper cam ring 230 at positions approximately 180° apart in the circumferential direction but unintentionally. The locking protrusions 235 are flat or curved plate-shaped portions that are substantially perpendicular to the radial direction. The locking protrusions 235 are engaged (fitted) with the locking recesses 302 of the clutch dial 300 described later. As a result, the front stopper cam ring 230 rotates together with the clutch dial 300.

[0117] The transmission / output structure 4 includes a nut 260 as a screw member. The nut 260 is made of resin, for example.

[0118] like Fig.14 As shown in (A) to (E), the nut 260 has a threaded portion 261 , six spring locking holes 262 , and three notch portions 263 .

[0119] The threaded portion 261 is provided on the outer peripheral surface of the nut 260 and is screwed with the threaded portion 301 of the clutch dial 300 described later. The six spring locking holes 262 are non-through holes arranged at equal angles in the circumferential direction and are respectively held Figure 5 to Figure 7 The three cutouts 263 are arranged at equal angles in the circumferential direction and are provided respectively with Figure 5 to Figure 7 The screw 133 that appears in passes through.

[0120] Figure 6-7 The thrust plate 165 is made of metal, for example, and is urged rearward relative to the nut 260 by the clutch spring 250, thereby pushing 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 the pin sleeve 161 held in the through hole 143 of the gear case 140.

[0121] The transmission / output structure 4 includes a ratchet cam ring 280 as a cam ring. The ratchet cam ring 280 is made of metal, for example.

[0122] like Fig.15As shown in (A) to (G), the ratchet cam ring 280 has an outer peripheral side protrusion 282 , an inner peripheral side protrusion 284 , three rotation-stopping protrusions 285 , and three small protrusions 288 .

[0123] The outer circumferential side protrusion 282 protrudes forward from the radially outer side portion of the ratchet cam ring 280. The outer circumferential side protrusion 282 is a flat plate-shaped or curved plate-shaped portion substantially perpendicular to the radial direction.

[0124] The inner circumferential side protrusion 284 protrudes forward from the radially inner portion of the ratchet cam ring 280. The inner circumferential side protrusion 284 is a flat plate or a curved plate-like portion substantially perpendicular to the radial direction.

[0125] The three anti-rotation protrusions 285 are arranged at equal angles in the circumferential direction and protrude toward the center of the ratchet cam ring 280. The anti-rotation protrusions 285 are clamped in the gap between the two forked anti-rotation parts 144 of the gear box 140. Thus, the ratchet cam ring 280 cannot rotate relative to the gear box 140. The back surface of the anti-rotation protrusion 285 contacts the front surface of the outer protrusion 372 of the clutch hub 370 described later and is pushed forward.

[0126] Three small protrusions 288 protrude radially inwardly from one of the anti-rotation protrusions 285 at a predetermined angle in the circumferential direction. The small protrusions 288 contact the outer circumferential surface of the threaded boss portion 345 of the front shell 340 described later at the point where the circumferential position of the anti-rotation protrusion 285 coincides with the circumferential position of the outer protrusion 372 of the clutch hub 370, thereby having a positioning function in the circumferential direction.

[0127] When the ratchet cam ring 280 is set in front of the clutch hub 370, the outer protrusion 372 of the clutch hub 370 is passed through the gap between the circumferential anti-rotation protrusion 285 and the small protrusion 288. Then, the ratchet cam ring 280 is rotated until the small protrusion 288 contacts the outer circumferential surface of the threaded boss portion 345 of the front shell 340, and the back surface of the anti-rotation protrusion 285 contacts the front surface of the outer protrusion 372 of the clutch hub 370 by the force applied by the ratchet spring 360.

[0128] The transmission / output structure 4 includes a clutch dial 300 as a switching operation portion. The clutch dial 300 is made of resin, for example.

[0129] like Fig.16 As shown in (A) to (F), the clutch dial 300 has a threaded portion 301 , two locking recesses 302 , an inner peripheral side recess 304 , an outer peripheral side hole 305 , a cylindrical portion 306 , a front wall portion 307 , and a leaf spring mounting portion 308 .

[0130] The central axis of the cylindrical portion 306 is coaxial with the motor shaft 31 , and the cross section perpendicular to the front-rear direction is substantially circular, with the diameter decreasing toward the front. The front wall portion 307 extends radially inward from the front end of the cylindrical portion 306 .

[0131] The threaded portion 301 is provided on the inner circumferential surface of the cylindrical portion 306. The threaded portion 301 is screwed with the threaded portion 261 of the nut 260. The clutch dial 300 is clamped in the front-to-back direction by the gear box 140 and the front housing 340 described later, so that the front-to-back position is fixed. Therefore, the nut 260 moves in the front-to-back direction in conjunction with the rotation of the clutch dial 300.

[0132] The two locking recesses 302 are located approximately 180° apart from each other in the circumferential direction and are respectively formed as cutouts formed by partially cutting away the lower end of the threaded portion 301. The locking recesses 302 are engaged with the locking protrusions 235 of the front stopper cam ring 230, and the front stopper cam ring 230 rotates together with the clutch dial 300.

[0133] The inner concave portion 304 is located radially inside the back surface of the front wall portion 307. The radial position of the inner concave portion 304 is equal to the radial position of the inner protrusion 284 of the ratchet cam ring 280 (or includes the radial position range of the inner protrusion 284).

[0134] The outer hole 305 penetrates the radially outer portion of the front wall 307 in the front-rear direction. The radial position of the outer hole 305 is equal to the radial position of the outer protrusion 282 of the ratchet cam ring 280 (or includes the radial position range of the outer protrusion 282).

[0135] The leaf spring mounting portion 308 is provided for mounting Figure 6-7 The portion of the leaf spring 331 (eg, made of metal) that appears in the.

[0136] The transmission / output structure 4 includes a front shell 340 as an output housing. The front shell 340 is made of metal, for example.

[0137] like Fig.17 As shown in (A) to (E), the front shell 340 has a large diameter cylindrical portion 341, a small diameter cylindrical portion 342, a connecting surface portion 343, three cutout portions 344, three threaded boss portions 345, three screw holes 346, three screw holes 347, a bearing retaining portion 348, two anti-rotation protrusions 349, two anti-slip protrusions 350, and a locking recess 351.

[0138] The large diameter cylinder 341 is a cylindrical portion coaxial with the motor shaft 31. The small diameter cylinder 342 is a cylindrical portion coaxial with the motor shaft 31. The diameter of the small diameter cylinder 342 is smaller than that of the large diameter cylinder 341, and is located further back than the large diameter cylinder 341. The ratchet spring 360, the rear ratchet 410, the front ratchet 440, the ball bearing 461, etc. are arranged in the small diameter cylinder 342. The connecting surface portion 343 is a wall portion perpendicular to the front-rear direction that connects the rear end portion of the large diameter cylinder 341 and the front end portion of the small diameter cylinder 342.

[0139] The three cutouts 344 are arranged at equal angles in the circumferential direction, and are respectively provided to allow the outer protrusions 372 of the clutch hub 370 described later to pass through. The three threaded bosses 345 are arranged at equal angles in the circumferential direction, and are respectively provided to protrude radially outward from the outer circumferential surface of the small diameter cylinder 342. The three screw holes 347 are respectively non-through holes opened on the back side of the threaded bosses 345, and are respectively connected to the outer side of the clutch hub 370. Figure 5 to Figure 7 The screw 133 is screwed in. The threaded boss portion 345 and the screw hole 347 correspond to the mounting portion on the output housing side.

[0140] The three screw holes 346 are non-through holes opened on the front surface of the connecting surface 343 and are respectively connected to Figure 5 to Figure 7 The three screw holes 346 are arranged at the same position as the three screw holes 347 in the circumferential direction. The bearing holding portion 348 holds Figure 5 to Figure 7 The ball bearing 335 (bearing) appears in the . The ball bearing 335 is made of metal, for example, and supports the rear part of the main shaft 470 in a rotatable manner.

[0141] The two anti-rotation protrusions 349 are located at positions approximately 180° apart from each other in the circumferential direction, and protrude radially outward from the left and right portions of the outer circumferential surface of the large-diameter cylindrical portion 341. The anti-rotation protrusions 349 are rotation limiting portions, which engage (fit) with the first anti-rotation recess 616 or the second anti-rotation recess 617 of the sub-handle 600 described later, thereby limiting the rotation of the sub-handle 600 relative to the front shell 340.

[0142] The two anti-slip protrusions 350 are located at positions approximately 180° apart from each other in the circumferential direction, and protrude radially outward from the left and right portions of the outer circumferential surface of the large-diameter cylindrical portion 341, respectively. The protruding length of the anti-slip protrusion 350 is shorter than the protruding length of the anti-rotation protrusion 349. The anti-slip protrusion 350 is continuous from the anti-rotation protrusion 349 to both sides in the circumferential direction. The anti-slip protrusion 350 prevents the sub-handle 600 described later from slipping out (detaching) from the front shell 340 in the forward direction.

[0143] The locking recess 351 is a groove portion for the plate spring 331 to be embedded, and has locking recesses corresponding to the various levels of the set tightening torque of the clutch mode, a locking recess corresponding to the electric drill mode, and a locking recess corresponding to the vibration mode. The rotational position of the clutch dial 300 is determined by embedding the plate spring 331 in the locking recess 351, and the clutch dial 300 is locked in the rotation direction, so that it is held so as not to rotate accidentally.

[0144] The transmission / output structural portion 4 includes a clutch hub 370 .

[0145] The clutch hub 370 is a restriction portion that restricts the movement (rotation) of the rear ratchet 410 in the vibration mode. The clutch hub 370 is made of metal, for example.

[0146] like Fig.18 As shown in (A) to (E), the clutch hub 370 includes an annular portion 371 , three outer protruding portions 372 , and six locking protrusions 373 .

[0147] The annular portion 371 is a ring portion coaxial with the motor shaft 31. The three outer protrusions 372 are arranged at equal angles in the circumferential direction and protrude radially outward from the outer circumferential surface of the annular portion 371. The six locking protrusions 373 are protrusions arranged at equal angles in the circumferential direction and protrude radially inward from the rear portion of the inner circumferential surface of the annular portion 371.

[0148] The transmission / output structure 4 includes a rear ratchet 410 as a second vibration part. The rear ratchet 410 is made of metal, for example.

[0149] like Fig.19 As shown in (A) to (F), the rear ratchet 410 is annular and has a concave-convex portion 411 on the front surface and six locking protrusions 412 on the front portion of the outer peripheral surface. The six locking protrusions 412 are protrusions arranged at equal angles in the circumferential direction and protruding radially outward.

[0150] Figure 6 and Figure 7 The thrust bearing 391 and the bearing washer 395 are made of metal, for example, and are interposed between the back surface of the rear ratchet 410 and the surface of the front shell 340 facing it, and bear the load in the front-back direction. The thrust bearing 391 and the bearing washer 395 reduce the friction when the top tool 20 is pressed against the other material for use, thereby suppressing power loss.

[0151] The transmission / output structure 4 includes a front ratchet 440 as a first vibration part. The front ratchet 440 is made of metal, for example.

[0152] like Fig. 20As shown in (A) to (F), the front ratchet 440 is annular and has a concavoconvex portion 441 on the back. The concavoconvex portion 441 is a vibration generating shape portion and outputs vibration to the main shaft 470 by contacting and relatively rotating with the concavoconvex portion 411 (vibration generating shape portion) of the rear ratchet 410.

[0153] Figure 5 to Figure 7 The spring 431 is made of metal, for example, and applies force to the front ratchet 440 forward relative to the rear ratchet 410. Thus, when the top tool 20 is not pressed against the other material, the rear ratchet 410 and the front ratchet 440 are in non-contact, and the generation of vibration can be suppressed. The ratchet washer 435 is made of metal, for example, and avoids contact between the front ratchet 440 and the spring 431 to reduce friction.

[0154] Figure 5 to Figure 7 The ball bearing 461 shown in the front housing 340 is made of metal, for example, and supports the middle portion of the front ratchet 440 and the main shaft 470 so as to be rotatable relative to the front housing 340. The front ratchet 440 and the main shaft 470 rotate integrally.

[0155] The transmission / output structure 4 includes a main shaft 470 and a chuck 500. The main shaft 470 and the chuck 500 are both made of metal, for example. The main shaft 470 is driven to rotate by the motor 30 via the transmission mechanism 50. The chuck 500 holds Figure 3 The top tool 20 appears in the middle and rotates integrally with the main shaft 470.

[0156] The threaded portion of the rear inner circumference of the chuck 500 is screwed with the threaded portion of the front outer circumference of the spindle 470, so that the chuck 500 is fixed to the spindle 470. In addition, the chuck 500 is fixed to the spindle 470 by a left screw 495 (for example, made of metal). The spindle 470 and the chuck 500 are firmly fixed to each other, thereby forming a substantially integrated top tool holding portion.

[0157] Figure 5 to Figure 7 The bearing cover 485 shown in the figure is made of metal, for example, and is fixed to the front housing 340 by means of screws 489 that penetrate through holes 487 of the bearing cover 485 and are screwed into screw holes 346 of the front housing 340 .

[0158] Figure 5 to Figure 7 The O-ring 481 is an elastic body such as rubber, and is provided between the inner peripheral surface of the bearing cover 485 and the outer peripheral surface of the main shaft 470. The O-ring 481 slides on the inner peripheral surface of the bearing cover 485 to reduce the impact when the rotating hand stops (when braking). The O-ring 481 also has the function of preventing oil leakage.

[0159] Figure 5 to Figure 7The retaining ring 483 shown in the figure is made of metal, for example, and is provided on the inner peripheral surface of the small-diameter cylindrical portion 342 of the front housing 340 , and functions as a stopper for the ball bearing 461 .

[0160] (Decomposability of the transmission / output structure 4) Fig.21 It is a right side cross-sectional view showing a state where the transmission / output structure section 4 is separated into the transmission section 5 , the output switching section 6 , and the output section 7 .

[0161] The transmission unit 5 is located in front of the motor 30 and transmits the driving force of the motor 30 to the main shaft 470. The transmission unit 5 includes a transmission unit housing (motor spacer 40, rear housing 60, gear box 140) and various parts (transmission mechanism 50, etc.) held or supported by the transmission unit housing.

[0162] The output switching unit 6 switches the output of the output unit 7, that is, the presence or absence of torque or vibration. The output switching unit 6 is sandwiched between the output unit 7 and the transmission unit 5 in the front-rear direction. The output switching unit 6 includes a clutch dial 300 and various parts (nut 260, etc.) held or supported by the clutch dial 300.

[0163] The output unit 7 includes the front housing 340 and various parts held or supported by the front housing 340 , namely, the spindle 470 or the chuck 500 , the ball bearing 335 , the ball bearing 461 , and the like.

[0164] The transmission unit 5 is detachably assembled to the output unit 7 from the rear side. Specifically, the gear box 140 is assembled to the front case 340 from the rear side by screws 133 that penetrate through holes 145 of the gear box 140 and are screwed into screw holes 347 of the front case 340 .

[0165] The screw 133 is an example of a fixing portion that fixes the output unit 7 and the transmission unit 5. The screw 133 at least partially overlaps with the range of the output switching unit 6. If the fixing by the screw 133 is released, the transmission unit 5 can be removed from the output unit 7.

[0166] If the transmission unit 5 is removed from the output unit 7 , that is, if the screws 133 are removed and the gear box 140 is removed from the front housing 340 , the output switching unit 6 can be removed rearward from the output unit 7 while the spindle 470 and the chuck 500 are fixed.

[0167] (Clutch Mode, Drill Mode, Vibration Mode) The working machine 1 has a clutch mode, a drill mode, and a vibration mode, and any one of the modes can be selected by operating the clutch dial 300.

[0168] The clutch mode is a mode in which the transmission mechanism 50 cuts off the rotation transmission to the main shaft 470 when the set tightening torque (predetermined torque) is exceeded, that is, a mode in which the clutch mechanism is effective. The set tightening torque can be adjusted in a plurality of levels, for example, 22 levels, by operating the clutch dial 300.

[0169] Fig.23 (A) to (E) show the state when the clutch mode is set and the tightening torque is set to the minimum. Fig.24 (A) to (E) show the state when the clutch mode is set and the tightening torque is set to the maximum.

[0170] The clutch mechanism stops the rotation of the final ring gear 90 before the set tightening torque, and allows the rotation of the final ring gear 90 when the set tightening torque is reached or exceeded. The clutch mechanism includes a nut 260 , a clutch spring 250 , a thrust plate 165 , and a clutch pin 131 .

[0171] If a load (torque) is applied to the top tool 20 during the driving process of the motor 30, the final ring gear 90 that is not fixed will rotate. Before the tightening torque is set, the clutch pin 131 is located in the front surface recess 96 of the final ring gear 90. As a result, the final ring gear 90 cannot rotate, and the torque transmission by the transmission mechanism 50 is effective.

[0172] On the other hand, if the torque applied to the top tool 20 increases and exceeds the set tightening torque, that is, if the clutch pin 131 pushes the final ring gear 90 backward and applies a load (torque) greater than the force to stop the rotation of the final ring gear 90 to the final ring gear 90, the final ring gear 90 rotates and the clutch pin 131 goes over the front surface convex portion 95 of the final ring gear 90. This is a clutch action, and the torque transmission by the transmission mechanism 50 is cut off by the clutch mechanism.

[0173] The load (set tightening torque) when the clutch mechanism is operated is proportional to the compression amount of the clutch spring 250. When the clutch dial 300 is rotated, the nut 260 moves back and forth, and the compression amount of the clutch spring 250 can be changed.

[0174] exist Fig.23 In the states (A) to (E), the nut 260 is at the forward limit position, and the compression amount of the clutch spring 250 is minimal (the tightening torque is set to the minimum). When the nut 260 is rotated clockwise from the front, the nut 260 moves backward, and the compression amount of the clutch spring 250 increases. Fig.24 In the states (A) to (E), the nut 260 is at the rearward limit position, and the compression amount of the clutch spring 250 is maximum (the set tightening torque is the highest).

[0175] (Switching Structure to Drill Mode) The drill mode is a mode in which the clutch mechanism is not used and the final ring gear 90 is made non-rotatable, and is a mode in which the maximum tightening torque can be generated as the working machine 1.

[0176] If from Fig.24 From the state (A) to (E), that is, the state in which the clutch mode is set and the tightening torque is set to the highest, the clutch dial 300 is further rotated clockwise as viewed from the front to a rotation position corresponding to the electric drill mode, and the state becomes Fig.25 The states (A) to (E) are the electric drill modes.

[0177] The switching structure to the electric drill mode includes a stopper block 120 , a stopper spring 117 as a biasing member, a rear stopper cam ring 210 , and a front stopper cam ring 230 .

[0178] The stopper 120 can move between a locking position (advanced position) and a non-locking position (retracted position), and when in the locking position, the final ring gear 90 cannot rotate. The front end of the stopper 120 protrudes further forward than the final ring gear 90. The stopper spring 117 is made of metal, for example, and urges the stopper 120 forward, that is, toward the locking position.

[0179] The clutch dial 300 is a switching operation unit that can switch the position of the stopper 120 between the locking position and the non-locking position. The clutch dial 300 is located in front of the final ring gear 90. The clutch dial 300 is rotatable around the extension of the axis of the motor shaft 31.

[0180] 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 non-locking position to the locking position against the biasing force of the stopper spring 117. By operating the clutch dial 300, the restriction and release of the restriction by the rear stopper cam ring 210 and the front stopper cam ring 230 can be switched. That is, the rear stopper cam ring 210 and the front stopper cam ring 230 constitute a cam mechanism that moves the stopper block 120 between the non-locking position and the locking position in conjunction with the rotation of the clutch dial 300.

[0181] The rear stop cam ring 210 is located in front of the stop block 120, and the back surface is in contact with the stop block 120. The rear stop cam ring 210 is in contact with the stop block 120 on the outside of the final ring gear 90 in the radial direction of the final ring gear 90. The rear stop cam ring 210 is located further in front of the final ring gear 90. The rear stop cam ring 210 is urged forward by the stop spring 117 via the stop block 120. The rotation of the rear stop cam ring 210 relative to the gear box 140 is restricted by the engagement (fitting) of the stop convex portion 148 and the stop convex portion 149 of the gear box 140 with the stop concave portion 218 and the stop concave portion 219 of the rear stop cam ring 210.

[0182] 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 by the engagement (fitting) of the engagement protrusion 235 of the front stopper cam ring 230 with the engagement recess 302 of the clutch dial 300. When the clutch dial 300 reaches a rotation position corresponding to the electric drill mode, that is, when the front stopper cam ring 230 reaches a predetermined rotation position, the rear stopper cam ring 210 moves forward. As a result, the movement restriction of the stopper 120 from the non-engaged position to the engaged position is released.

[0183] The rear stopper cam ring 210 has an outer circumferential inclined portion 212 and an outer circumferential flat portion 213 as recessed portions, and an inner circumferential inclined portion 214 and an inner circumferential flat portion 215 as recessed portions. The front stopper cam ring 230 has an outer circumferential protrusion 232 and an inner circumferential protrusion 234 as protrusions. In the process of the front stopper cam ring 230 reaching a predetermined rotational position (the process of the clutch dial 300 reaching a rotational position of the electric drill mode), the outer circumferential protrusion 232 and the inner circumferential protrusion 234 descend from 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 may be steeper than the inclination of the threaded portion 301 of the clutch dial 300.

[0184] exist Fig.24 (A)~(E) and Fig.25In (A) to (E), during the process of switching from the clutch mode to the electric drill mode, the outer peripheral protrusion 232 of the front stop cam ring 230 descends from the outer peripheral inclined portion 212 of the rear stop cam ring 210, and the rear stop cam ring 210 moves forward due to the force of the stop spring 117, and the stop block 120 moves to the locked position (advanced position). In the electric drill mode, the locking protrusion 123 of the stop block 120 in the locked position engages with the outer peripheral protrusion 91 of the final ring gear 90 (contacts in the rotation direction) to prevent the final ring gear 90 from rotating. In addition, the locking protrusion 123 of the stop block 120 in the non-locking position does not engage with the outer peripheral protrusion 91 of the final ring gear 90, allowing the final ring gear 90 to rotate.

[0185] When the clutch dial 300 is within the prescribed rotation range corresponding to the clutch mode ( Fig.23 (A)~(E) status and Fig.24 When the front stop cam ring 230 reaches the rotation position between the states (A) and (E), the outer protrusion 232 and the inner protrusion 234 of the front stop cam ring 230 abut against the flat portion 211 of the rear stop cam ring 210, the rear stop cam ring 210 cannot move forward, and the stop block 120 does not move to the locking position.

[0186] (Switching Structure to Vibration Mode) The vibration mode is a mode in which vibration in the front-rear direction is applied to the spindle 470 in the electric drill mode.

[0187] If from Fig.25 From the state (A) to (E), that is, the electric drill mode, the clutch dial 300 is further rotated clockwise as viewed from the front to a rotation position corresponding to the vibration mode, and then Fig.26 The states (A) to (E) are vibration modes.

[0188] The switching structure to the electric 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 .

[0189] 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 main shaft 470. The front ratchet 440 is driven (rotated) by the driving force of the motor 30. The clutch dial 300 switches the vibration-on state and the vibration-off state of the rear ratchet 410 and the front ratchet 440.

[0190] The ratchet cam ring 280 and the clutch hub 370 are vibration switching parts that move from a vibration off position (retracted position) to a vibration on position (advanced position) according 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 the clutch hub 370 forward, that is, toward the vibration on position.

[0191] exist Fig.15 The outer circumferential protrusion 282 and the inner circumferential protrusion 284 of the ratchet cam ring 280 shown in (A) to (E) and (G), and Fig.16 The inner circumferential recess 304 and the outer circumferential hole 305 of the clutch dial 300 shown in (A) to (C) and (E) are guide portions, which guide the ratchet cam ring 280 and the clutch hub 370 to move from the vibration disconnection position to the vibration connection position when the clutch dial 300 reaches a rotational position corresponding to the vibration mode.

[0192] When the clutch dial 300 reaches the rotation position corresponding to the vibration mode, the outer circumferential protrusion 282 of the ratchet cam ring 280 faces the outer circumferential hole 305 of the clutch dial 300, and the inner circumferential protrusion 284 of the ratchet cam ring 280 faces the inner circumferential recess 304 of the clutch dial 300. Furthermore, the outer circumferential protrusion 282 and the inner circumferential protrusion 284 of the ratchet cam ring 280 enter the outer circumferential hole 305 and the inner circumferential recess 304 of the clutch dial 300, respectively, and thus, the ratchet cam ring 280 and the clutch hub 370 are moved from the vibration disconnection position to the vibration connection position by the force of the ratchet spring 360.

[0193] The outer circumferential protrusion 282 and the inner circumferential protrusion 284 of the ratchet cam ring 280 are provided at one circumferential end portion thereof. Fig.15 The inclined portion 286 and the inclined portion 287 shown in (G) play a role in allowing the outer circumferential side protrusion 282 and the inner circumferential side protrusion 284 to smoothly enter and exit the outer circumferential side hole 305 and the inner circumferential side recess 304 of the clutch dial 300, respectively.

[0194] The clutch hub 370 does not restrict the movement of the rear ratchet 410 at the vibration disconnection position, and restricts the movement of the rear ratchet 410 at the vibration connection position. The front ratchet 440 is driven by the driving force of the motor 30 with respect to the rear ratchet 410 whose movement is restricted, thereby generating vibration.

[0195] The clutch hub 370 is urged forward by the ratchet spring 360 and presses the ratchet cam ring 280 forward. Fig.18 The locking projection 373 of the clutch hub 370 shown in (A) to (D) and Fig.19The locking projection 412 of the rear ratchet wheel 410 shown in (A) to (C) and (E) to (F) is formed when the clutch hub 370 is in the vibration-connected position. Fig. 22 (C) and Fig.26 (D) and engage with each other.

[0196] like Fig. 22 As shown in (B) and (C), the locking protrusion 373 of the clutch hub 370 and the locking protrusion 412 of the rear ratchet 410 are provided with inclined portions 374 and 413 on both sides of the circumference, and the inclined portions 374 and 413 make it difficult for the clutch hub 370 to move from the vibration-on position to the vibration-off position. Fig. 22 The angle θ shown in (B) and (C) is represented by θ / 2 with respect to the front-rear direction. When the clutch hub 370 is in the vibration-on position, the locking protrusion 373, the inclined portion 374 of the locking protrusion 412, and the inclined portion 413 are in contact with each other. If a force in the rotational direction is applied to the rear ratchet 410 in this state, a force in the forward direction is applied to the clutch hub 370 by the engagement of the inclined portion 374 and the inclined portion 413, so that the clutch hub 370 is not easily moved to the vibration-off position.

[0197] exist Fig.25 (A)~(E) and Fig.26 In (A) to (E), during the process of switching from the electric drill mode to the vibration mode, the ratchet cam ring 280 and the clutch hub 370 are moved forward by the force of the ratchet spring 360, and the locking protrusion 373 of the clutch hub 370 and the locking protrusion 412 of the rear ratchet 410 are aligned in the front-to-back direction. In this process, the outer circumferential protrusion 232 and the inner circumferential protrusion 234 of the front stop cam ring 230 move on the outer circumferential flat portion 213 and the inner circumferential flat portion 215 of the rear stop cam ring 210, thereby effectively maintaining the rotation restriction of the final ring gear 90 by the stop block 120.

[0198] When the clutch dial 300 is within the prescribed rotation range corresponding to the clutch mode and the electric drill mode ( Fig.23 (A)~(E) status and Fig.25 (A) to (E)), the outer protrusion 282 and the inner protrusion 284 of the ratchet cam ring 280 abut against the flat portion (the plane portion perpendicular to the front-to-back direction) of the clutch dial 300, so that the ratchet cam ring 280 and the clutch hub 370 do not move forward (do not move to the vibration-connected position).

[0199] (How the shift arm 71 is inserted) As described above, the motor spacer 40, the rear housing 60, and the gear box 140 are fixed by four screws 44 to form a transmission housing. This improves the rigidity of the transmission housing as a whole, and can suppress deformation during operation of the clutch mechanism, for example.

[0200] On the other hand, in a structure in which the shift arm 71 passes through the outside of the screw 44 in the radial direction of the rear housing 60 and extends to the guide hole 64 of the rear housing 60, the motor housing portion 11 covered on the outside of the shift arm 71 is enlarged, resulting in an increase in the size of the product.

[0201] like Figure 27 to Figure 30 As shown, in the working machine 1 , the speed change arm 71 is passed through the inner side of the screw 44 in the radial direction of the rear housing 60 and extends to the guide hole 64 of the rear housing 60 .

[0202] When the motor spacer 40 , the rear housing 60 , and the gear box 140 are fixed by the two upper screws 44 , there is a gap between the outer surface of the rear housing 60 and the two upper screws 44 , and the shift arm 71 extends in the gap.

[0203] The portions of the two upper screws 44 extending in the front-rear direction on the outside of the rear housing 60 are inserted into the screw sleeve 45 which is a cylindrical portion separate from the rear housing 60. That is, the two upper screws 44 respectively penetrate the screw insertion holes 43 of the motor spacer 40 and the screw sleeve 45, and are screwed into the screw holes 151 of the gear box 140. The screw sleeve 45 is used to prevent the motor spacer 40 from being bent or damaged due to over-tightening of the two upper screws 44. The speed change arm 71 passes through the gap between the outer peripheral surface of the screw sleeve 45 and the outer peripheral surface of the rear housing 60.

[0204] The two screws 44 on the lower side respectively penetrate the screw insertion hole 43 of the motor spacer 40 and the through hole 67 of the rear shell 60, and are screwed to the screw hole 151 of the gear box 140. The threaded boss portion 62 having the through hole 67 is a part of the rear shell 60 (integrated with the rear shell 60), and there is no gap between the threaded boss portion 62 and the outer surface of the rear shell 60, but this is not the part where the speed change arm 71 is to pass through, so there is no problem of enlargement.

[0205] (Sub-handle 600) Figure 31 to Figure 39 This relates to the sub-handle 600 of the present embodiment. Figure 31 to Figure 34 , Fig.39 The working machine 1 is shown to be equipped with a sub-handle 600 . Figure 35 to Figure 38 The front housing 340 is a handle mounting portion of the working machine 1. In addition, the sub-handle 600 is not limited to the sub-handle 600. Fig.31 The installation form in which the working machine 1 is extended in the left direction as in the above example may also be an installation form in which the working machine 1 is extended in the right direction.

[0206] (Opening and Closing Structure of the Mounting Portion 601) The sub-handle 600 includes a mounting portion 601, a first shaft portion 602, and a second shaft portion 603.

[0207] The mounting portion 601 is annular with a gap 614 in a part of the circumference, and is engaged with the front housing 340 of the working 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.

[0208] The first cylindrical portion 612 is disposed on the upper portion of the annular portion 615 and is disposed on one side ( 100 ft ) of the gap 614 in the length direction (hereinafter referred to as the “gap length direction”) of the gap 614. Fig.35 ), and extends along the length of the gap.

[0209] The first cylindrical portion 612 has a head holding portion 624 and a shaft insertion portion 626. The head holding portion 624 holds the head 610 of the first shaft portion 602. The head holding portion 624 is located on one side of the shaft insertion portion 626 in the gap length direction ( Fig.35 The shaft insertion portion 626 is larger than the shaft insertion portion 626 when viewed from the gap length direction and is non-circular, for example, hexagonal, for the head 610 to be embedded. The shaft insertion portion 626 is smaller than the head 610 when viewed from the gap length direction and allows the shaft 611 of the first shaft rod portion 602 to pass through.

[0210] The second cylindrical portion 613 is disposed on the upper portion of the annular portion 615 and is disposed on one side of the gap 614 in the gap length direction ( Fig.35 The central axis of the first cylindrical portion 612 and the second cylindrical portion 613 is parallel to the gap length direction.

[0211] The second cylindrical portion 613 has a shaft insertion portion 627 and an enlarged diameter portion 628. The shaft insertion portion 627 allows the shaft portion 611 of the first shaft portion 602 to pass through. The enlarged diameter portion 628 is located on the other side of the shaft insertion portion 627 in the gap length direction ( Fig.35 The pin layer through hole 606 is formed on the right side of the pin layer 628, 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 the end of the second shaft portion 603 is inserted. The pin layer through hole 606 faces the inside of the enlarged diameter portion 628. The pin layer through hole 606 opens in a direction intersecting the gap length direction.

[0212] The annular portion 615 has two first anti-rotation recesses 616 and ten second anti-rotation recesses 617 on the inner circumference. The two first anti-rotation recesses 616 are arranged about 180° apart in the circumferential direction of the mounting portion 601. The two first anti-rotation recesses 616 face each other across the center of the mounting portion 601. The ten second anti-rotation recesses 617 are arranged five each between the two first anti-rotation recesses 616 at equal angles in the circumferential direction of the mounting portion 601. The length of the first anti-rotation recess 616 in the circumferential direction of the mounting portion 601 is longer than that of the second anti-rotation recess 617.

[0213] A depth gauge (not shown) can be mounted on the sub-handle 600 , and the knob bolt 605 is used to fix the depth gauge.

[0214] 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 a natural length. The natural length is the length of the gap 614 when no external force is applied to the mounting portion 601 to expand or reduce the gap 614.

[0215] The first shaft portion 602 extends along the gap length direction and is located on one side ( Fig.35 The first shaft portion 602 passes through the gap 614 and protrudes from the mounting portion 601 to the other side in the gap length direction.

[0216] The second shaft portion 603 extends along the gap length direction and is located at the other side of the gap 614 in the gap length direction ( Fig.35 The second shaft portion 603 protrudes from the mounting portion 601 to the other side in the length direction.

[0217] The first shaft portion 602 and the second shaft portion 603 are engaged with each other so as to be relatively movable in the gap length direction. By moving the second shaft portion 603 relative to the first shaft portion 602 in the gap length direction, the length of the gap 614 can be adjusted.

[0218] The first shaft portion 603 and the second shaft portion 603 are threadedly engaged with each other. By rotating the second shaft portion 603 relative to the first shaft portion 602 , the second shaft portion 603 can be relatively moved along the length direction relative to the first shaft portion 602 .

[0219] The first shaft portion 602 has a head portion 610 and a shaft portion 611. The head portion 610 is located on one side of the shaft portion 611 in the gap length direction, and is larger than the shaft portion 611 in the gap length direction and is non-circular, for example, hexagonal. The head portion 610 is embedded in the head holding portion 624 of the mounting portion 601, so that the first shaft portion 602 cannot rotate relative to the mounting portion 601, and the first shaft portion 602 will not move from the mounting portion 601 to the other side in the gap length direction ( Fig.35 In addition, the first shaft portion 602 will not be disengaged from the mounting portion 601 to one side in the gap length direction (the right side). Fig.35 on the left side of the diagram) and then come out.

[0220] The shaft 611 extends from the head 610 to the other side in the gap length direction and passes through the shaft insertion portions 626 and 627 of the mounting portion 601 to reach the inside of the second shaft portion 603. The shaft 611 has an external thread 622 on its top end outer peripheral surface.

[0221] The second shaft portion 603 includes a handle portion 604 , a large diameter portion 618 , and a small diameter portion 619 in order from the other side in the gap length direction.

[0222] The small diameter portion 619 is inserted into the enlarged diameter portion 628 of the second cylindrical portion 613 of the mounting portion 601. The cross-sections of the small diameter portion 619 and the enlarged diameter portion 628 are both circular. The small diameter portion 619 has a pin insertion groove 620 and an O-ring insertion groove 621. The pin insertion groove 620 and the O-ring insertion groove 621 are groove portions that surround the outer circumference of the small diameter portion 619. The pin insertion groove 620 is located on one side of the O-ring insertion groove 621 in the gap length direction ( Fig.35 on the left side of the image).

[0223] The pin 607 inserted into the pin layer through hole 606 extends in the pin insertion groove 620. The pin layer through hole 606 is located at the same position as the pin insertion groove 620 in the gap length direction. The pin 607 is inserted into the pin layer through hole 606 and extends inside the pin insertion groove 620, so that the second shaft portion 603 is immovable relative to the second cylindrical portion 613 of the mounting portion 601 in the gap length direction.

[0224] The second shaft portion 603 is rotatable relative to the second cylindrical portion 613. An O-ring 609 is fitted in the O-ring fitting groove 621. The O-ring 609 generates friction 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.

[0225] The second shaft portion 603 has a nut portion 623 constituting an internal thread portion. The nut portion 623 is threadedly engaged with the external thread portion 622 of the first shaft portion 602. The nut portion 623 may be a separate part from the large diameter portion 618 and the small diameter portion 619, or may be an integral part. Fig.35 In the example of FIG. 6 , the nut portion 623 is a separate component from the large diameter portion 618 and the small diameter portion 619 .

[0226] When the handle portion 604 is turned, the entirety of the second shaft portion 603 rotates integrally relative to the mounting portion 601 and the first shaft portion 602. In conjunction with this, the second shaft portion 603 moves relative to the first shaft portion 602 in the gap length direction through the threaded engagement of the external threaded portion 622 of the first shaft portion 602 and the nut 623 of the second shaft portion 603. At this time, the second shaft portion 603 is engaged with the second cylindrical portion 613 of the mounting portion 601 via the pin 607, and the second cylindrical portion 613 moves relative to the first cylindrical portion 612 in the gap length direction. Thus, the length of the gap 614 is adjusted.

[0227] If from Fig.38 (B) and (E) show the state that the gap 614 is in the natural length. If the handle 604 is turned leftward, the second shaft 603 can be moved to the other side in the gap length direction ( Fig.38 The right side in the figure) moves relative to each other, thereby adjusting the length of the gap 614 to be longer than the natural length. Fig.38 (C) and (F) indicate the state where the length of the gap 614 is the largest, i.e., the state where the mounting portion 601 is opened to the greatest extent. The thread engagement length of the external 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 prescribed length that does not damage the mounting portion 601.

[0228] If from Fig.38 (B) and (E) show the state where the gap 614 is at its natural length. If the handle 604 is turned rightward, the second shaft 603 and the second cylindrical portion 613 of the mounting portion 601 can be moved to one side in the gap length direction ( Fig.35 The left side in the figure) moves relative to each other, thereby adjusting the length of the gap 614 to be shorter than the natural length. Fig.38 (A) and (D) show the state where the length of the gap 614 is the smallest, that is, the closed limit state of the mounting portion 601. By adjusting the length of the gap 614 to be shorter than the natural length, the mounting portion 601 can be tightened to the front shell 340, thereby fixing the sub-handle 600 to the front shell 340.

[0229] By making the gap 614 open to a greater extent than the natural length, the front shell 340 of the working machine 1 can be passed through the inner side of the mounting portion 601. The anti-slip protrusion 350 of the front shell 340 is large enough to prevent the mounting portion 601 from slipping out forward when the gap 614 is at the natural length. The anti-slip protrusion 350 suppresses (prevents) the mounting portion 601 from slipping out forward from the front shell 340 when the gap 614 is at the natural length or less.

[0230] (Easy-to-Store Structure of Sub-handle 600) To mount the sub-handle 600 on the front shell 340, the mounting portion 601 is fitted into the front shell 340 from the front while adjusting the length of the gap 614 to be longer than the natural length. Then, the handle portion 604 is turned rightward to reduce the gap 614.

[0231] When the sub-handle 600 is mounted on the front shell 340, the mounting angle can be selected from multiple levels. Two of the two first anti-rotation recesses 616 and the ten second anti-rotation recesses 617 of the mounting portion 601 corresponding to the mounting angle of the sub-handle 600 relative to the front shell 340 are engaged with the two anti-rotation protrusions 349 of the front shell 340.

[0232] 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 protrusion 349 of the front shell 340. The circumferential length of the second anti-rotation recess 617 of the mounting portion 601 is substantially equal to the circumferential length of the anti-rotation protrusion 349 of the front shell 340.

[0233] When the second anti-rotation recess 617 of the mounting portion 601 is engaged with the anti-rotation protrusion 349 of the front shell 340, the lengths of the two in the circumferential direction are substantially equal, so that the sub-handle 600 can be mounted on the front shell 340 without causing the sub-handle 600 to shake or with minimal shaking of the sub-handle 600. The second anti-rotation recess 617 of the mounting portion 601 is used when the sub-handle 600 is not stored, that is, when the working machine 1 is used.

[0234] When the first anti-rotation recess 616 of the mounting portion 601 is engaged with the anti-rotation protrusion 349 of the front shell 340, the sub-handle 600 can rotate within a predetermined angle range relative to the front shell 340 because the circumferential length of the first anti-rotation recess 616 is longer than the circumferential length of the anti-rotation protrusion 349. The first anti-rotation recess 616 is used when the sub-handle 600 is stored, that is, when the working machine 1 is not in use.

[0235] Fig.39 (A) to (C) are diagrams showing that the sub-handle 600 can rotate within a predetermined angle range in the stored state.

[0236] Fig.39(A) shows the state where the sub-handle 600 is rotated to the maximum extent in the counterclockwise direction in the figure. Fig.39 As shown in an enlarged manner in (B), this state is a first engagement state in which the first anti-rotation recess 616 of the mounting portion 601 and one end portion of the anti-rotation protrusion 349 of the front shell 340 in the circumferential direction are engaged with each other.

[0237] Fig.39 (B) indicates a state where the sub-handle 600 is in the center of the rotatable range. This state is a second engagement state in which the first anti-rotation recess 616 of the mounting portion 601 and one end side of the anti-rotation protrusion 349 of the front shell 340 in the circumferential direction do not contact each other. In addition, in the second engagement state, the first anti-rotation recess 616 of the mounting portion 601 and the other end side of the anti-rotation protrusion 349 of the front shell 340 in the circumferential direction can be engaged with each other.

[0238] Even when the first anti-rotation recess 616 of the mounting portion 601 is engaged with the anti-rotation protrusion 349 of the front shell 340, the friction force generated by the mounting portion 601 fastening the front shell 340 can be utilized to prevent the sub-handle 600 from rotating relative to the front shell 340 by making the gap 614 of the mounting portion 601 less than a specified length that is shorter than the natural length.

[0239] This embodiment has the following effects.

[0240] (1) The working machine 1 includes an output switching unit 6, which switches the output (the presence or absence of torque or vibration) of the output unit 7, and is clamped by the output unit 7 and the transmission unit 5. If the transmission unit 5 is removed from the output unit 7, the output switching unit 6 can be removed from the output unit 7 to the rear side. Specifically, if the screw 133 is removed and the gear box 140 is removed from the front shell 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 to the rear side. Therefore, even if the fixation of the main shaft 470 and the chuck 500 cannot be released, the components of the output switching unit 6, that is, the clutch dial 300 or the nut 260, the clutch spring 250 and other parts can be replaced, and the repairability is good.

[0241] As a comparison, a structure (hereinafter referred to as "Comparative Structure 1") in which the gear box 140 is extended forward to hold the ball bearings 335 and 461, and a retaining ring is used to prevent the clutch dial 300 from slipping forward relative to the gear box 140 is studied. In Comparative Structure 1, if the chuck 500 is not removed from the main shaft 470, the retaining ring cannot be approached, and the clutch dial 300 and the like cannot be removed forward or backward. Therefore, in Comparative Structure 1, when the clutch dial 300 and the like are damaged and need to be replaced, it is necessary to take measures such as removing the chuck 500 from the main shaft 470 using a special fixture or replacing the entire transmission / output structure 4, which increases the time or cost required for repair. The present embodiment is suitable for solving this problem.

[0242] (2) The transmission unit 5 and the output unit 7 can be commonly used in a plurality of models as modules, and thus are highly convenient.

[0243] (3) The working machine 1 includes: a transmission mechanism 50 including a final ring gear 90; a stopper 120 that prevents the final ring gear 90 from rotating when in the locked position; and a stopper spring 117 that applies force to the stopper 120 toward the locked position. Therefore, even if the front end of the convex portion 123 of the stopper 120 that is intended to move to the locked position contacts the rear end of the outer peripheral convex portion 91 of the final ring gear 90 and becomes unable to reach the locked position, if the final ring gear 90 rotates thereafter, the outer peripheral convex portion 91 moves from the front of the convex portion 123, and the stopper 120 automatically moves to the locked position. Therefore, it is possible to suppress the inconvenience of preventing the final ring gear 90 from rotating, that is, the inconvenience of failing to shift to the electric drill mode.

[0244] (4) The working machine 1 can switch the position of the stopper 120 between the locked position and the unlocked position by using the clutch dial 300. Specifically, when the clutch dial 300 is rotated to the rotation position of the electric drill mode, the stopper 120 moves to the locked position. Here, the moving force of the stopper 120 to the locked position is the force applied by the stopper spring 117, rather than the thread engagement based on the rotation of the clutch dial 300. Therefore, compared with the structure in which the nut 260 that moves forward and backward in conjunction with the rotation of the clutch dial 300 pushes the stopper pin toward the final ring gear 90, the inconvenience of not being able to rotate the clutch dial 300 to the rotation position of the electric drill mode can be suppressed, and the use is convenient.

[0245] (5) The stopper spring 117 is a structure for urging the stopper block 120 forward, and the stopper spring 117 and the stopper block 120 are provided at a position further rearward than the clutch dial 300. Therefore, compared with the case where the stopper spring 117 and the stopper block 120 are provided inside the clutch dial 300, the clutch dial 300 can be prevented from increasing in diameter, and the deterioration of the operability of rotating the clutch dial 300 can be prevented.

[0246] (6) The rear stopper cam ring 210 and the front stopper cam ring 230 function as a restriction portion that restricts the movement of the stopper 120 from the non-engaged position to the engaged position against the force applied by the stopper spring 117 when the clutch dial 300 is in the rotation range of the clutch mode. In addition, the rear stopper cam ring 210 and the front stopper cam ring 230 constitute a cam mechanism that moves the stopper 120 between the non-engaged position and the engaged position in conjunction with the rotation of the clutch dial 300 between the rotation position of the electric drill mode and the rotation position of the clutch mode. Therefore, the forward and backward movement of the stopper 120 (movement between the non-engaged position and the engaged position) that is limited to the rotation of the clutch dial 300 between the rotation position of the electric drill mode and the rotation position of the clutch mode and that is not based on the threaded engagement of the clutch dial 300 and the nut 260 can be appropriately realized.

[0247] (7) When the clutch dial 300 rotates between the rotation position of the electric drill mode and the rotation position of the clutch mode, the outer circumferential protrusion 232 and the inner circumferential protrusion 234 of the front stopper cam ring 230 move along the outer circumferential inclined portion 212 and the inner circumferential inclined portion 214 of the rear stopper cam ring 210. Here, by making the inclination angle of the outer circumferential inclined portion 212 and the inner circumferential inclined portion 214 steeper than the inclination of the threaded portion 301 of the clutch dial 300, the stopper 120 can be moved forward and backward to a greater extent in conjunction with the rotation of the clutch dial 300, compared with the case where the stopper 120 is moved by the threaded engagement of the clutch dial 300 and the nut 260. As a result, the amount of operation of the clutch dial 300 required for switching between the clutch mode and the electric drill mode can be reduced, and the use is convenient. In addition, since the outer circumferential inclined portion 212 and the inner circumferential inclined portion 214 form a recess, the outer circumferential protrusion 232 and the inner circumferential protrusion 234 of the front stop cam ring 230 can be easily inserted into and removed from the recess. This can prevent the clutch mode and the electric drill mode from being caught, making it easy to use.

[0248] (8) The rear stopper cam ring 210 is located further forward than the final ring gear 90, and the stopper 120 protrudes further forward than the final ring gear 90 and engages with the rear stopper cam ring 210. Thus, the switching structure to the electric drill mode (stopper 120, stopper spring 117, rear stopper cam ring 210, front stopper cam ring 230) is dispersedly arranged in front of and behind the final ring gear 90. Thus, unlike the case where the switching structure to the electric drill mode is arranged biased to one side of the front and rear of the final ring gear 90, it is easy to achieve a balance in the radial dimensions of the gear box 140 and the clutch dial 300, and the layout efficiency is good.

[0249] (9) In the working machine 1, when the clutch hub 370 reaches the vibration-on position, the clutch hub 370 restricts the movement of the rear ratchet 410. The front ratchet 440 is driven by the driving force of the motor 30 with respect to the rear ratchet 410 whose movement is restricted, thereby generating vibration. When the clutch dial 300 reaches the rotation position corresponding to the vibration mode, the outer circumferential protrusion 282 and the inner circumferential protrusion 284 of the ratchet cam ring 280 enter the outer circumferential hole 305 and the inner circumferential recess 304 of the clutch dial 300 along the inclined portion 286 and the inclined portion 287 respectively, and thus, the ratchet cam ring 280 and the clutch hub 370 are moved from the vibration-off position to the vibration-on position by the force of the ratchet spring 360. Therefore, compared with a structure in which the clutch hub 370 is pushed forward by the nut 260 that moves forward and backward in conjunction with the rotation of the clutch dial 300, the amount of operation of the clutch dial 300 required to switch the presence or absence of vibration can be reduced, which is convenient to use.

[0250] (10) Since the outer protrusion 282 and the inner protrusion 284 of the ratchet cam ring 280 have the inclined portions 286 and 287, the outer protrusion 282 and the inner protrusion 284 can smoothly enter and exit the outer hole 305 and the inner recess 304 of the clutch dial 300, thereby preventing the clutch dial 300 from getting caught when switching between the electric drill mode and the vibration mode, and facilitating use.

[0251] (11) The ratchet cam ring 280 and the clutch dial 300 function as a limiting portion that limits the movement of the clutch hub 370 from the vibration disconnection position to the vibration connection position against the force applied by the ratchet spring 360 when the clutch dial 300 is in the rotation range of the clutch mode and the electric drill mode. In addition, the ratchet cam ring 280 and the clutch dial 300 constitute a cam mechanism, and the cam mechanism moves the clutch hub 370 between the vibration disconnection position and the vibration connection 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 electric drill mode. Therefore, the front-back movement of the clutch hub 370 (movement between the vibration disconnection position and the vibration connection position) that is limited to the rotation of the clutch dial 300 between the rotation position of the vibration mode and the rotation position of the electric drill mode and that is not based on the threaded engagement of the clutch dial 300 and the nut 260 can be appropriately realized.

[0252] (12) Fig. 22 As shown in (B) and (C), the locking protrusion 373 of the clutch hub 370 and the locking protrusion 412 of the rear ratchet 410 are provided with inclined portions 374 and 413 on both sides of the circumference, and the inclined portions 374 and 413 make it difficult for the clutch hub 370 to move from the vibration-on position to the vibration-off position. If a force in the rotational direction is applied to the rear ratchet 410 at the vibration-on position, a force in the forward direction is applied to the clutch hub 370 by the engagement of the inclined portions 374 and 413, thereby making it difficult for the clutch hub 370 to move to the vibration-off position. In this way, it is possible to suppress the clutch hub 370 from being accidentally moved to the vibration-off position due to vibration or the like.

[0253] (13) The motor spacer 40, the rear housing 60, and the gear box 140 are fixed by four screws 44 and constitute a transmission housing with high rigidity, so that deformation of the clutch mechanism during operation can be suppressed. On the other hand, there is a gap between the outer surface of the rear housing 60 and the two upper screws 44, and the speed change arm 71 passes through the gap and extends to the guide hole 64 of the rear housing 60. Therefore, compared with a structure in which the speed change arm 71 passes through the outside of the screws 44 in the radial direction of the rear housing 60 and extends to the guide hole 64 of the rear housing 60, the size of the motor housing 11 covered on the outside of the speed change arm 71 can be suppressed, thereby suppressing the size of the product.

[0254] (14) The portions of the two upper screws 44 extending in the front-rear direction outside the rear housing 60 are inserted into the screw sleeve 45 which is a cylindrical portion separate from the rear housing 60. Therefore, the motor spacer 40 is prevented from being bent or damaged due to over-tightening of the two upper screws 44.

[0255] (15) The front shell 340 has the anti-falling protrusion 350 for the sub-handle 600, which can prevent the sub-handle 600 from falling out forward due to vibration during operation, etc., and improves the workability.

[0256] (16) The sub-handle 600 includes a mounting portion 601 that is annular and has a gap 614 in a portion of the circumference and that engages with the front shell 340 of the working machine 1, and is configured to be able to adjust the length of the gap 614 within a predetermined range including a length longer than the natural length. Therefore, even when the length of the gap 614 of the front shell 340 is the natural length and, for example, interferes with the anti-slip convex portion 350 of the front shell 340 and becomes difficult to attach and detach, by adjusting the length of the gap 614 to be longer than the natural length, attachment and detachment can be easily performed.

[0257] (17) The first shaft portion 602 and the second shaft portion 603 are threadedly engaged with each other, and the length of the gap 614 can be adjusted by rotating the handle portion 604 provided on the second shaft portion 603. Thus, the length of the gap 614 can be easily adjusted, and it is convenient to use.

[0258] (18) The pin 607 extending in the pin insertion groove 620 of the second shaft portion 603 makes the second shaft portion 603 immovable in the gap length direction relative to the second cylindrical portion 613 of the mounting portion 601. The pin 607 allows the second shaft portion 603 to rotate, so the operation of adjusting the length of the gap 614 by rotating the second shaft portion 603 is not hindered.

[0259] (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, thereby improving workability.

[0260] (20) The thread engagement length of the external 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 prescribed length that will not damage the mounting portion 601. Therefore, regardless of the degree of operation of the user, damage to the mounting portion 601 due to an excessively large gap 614 can be suppressed, and the use is convenient.

[0261] (21) The mounting portion 601 has a first anti-rotation recess 616 with a long circumferential length, and a second anti-rotation recess 617 with a short circumferential length. When the second anti-rotation recess 617 is engaged with the anti-rotation protrusion 349 of the front shell 340, since the circumferential lengths of the two are approximately equal, the sub-handle 600 can be installed on the front shell 340 without causing the sub-handle 600 to shake or the sub-handle 600 can shake to a minimum, thereby enabling stable operation. On the other hand, when the first anti-rotation recess 616 of the mounting portion 601 is engaged with the anti-rotation protrusion 349 of the front shell 340, since the circumferential length of the first anti-rotation recess 616 is longer than the circumferential length of the anti-rotation protrusion 349, the sub-handle 600 can be moved relative to the working machine 1 within a specified angle range in the stored state. Fig.39 (A) and (C) as shown, the installation state can be finely adjusted. Therefore, the workability of storing the sub-handle 600 in the working machine 1 is good. Fig.39 When the angle shown in (C) changes, the flange portion 625 of the handle portion 604 interferes with the battery pack 25 or the battery pack mounting portion 13, making it difficult to accommodate the battery pack. However, in this embodiment, this problem can be appropriately solved.

[0262] (22) Even when the first anti-rotation recess 616 of the mounting portion 601 is engaged with the anti-rotation projection 349 of the front shell 340, the frictional force generated by the mounting portion 601 fastening the front shell 340 can be used to prevent the sub-handle 600 from rotating relative to the front shell 340 by making the gap 614 of the mounting portion 601 smaller than the natural length and making the gap 614 smaller than the natural length smaller than the natural length. Therefore, the shaking of the sub-handle 600 in the stored state can be suppressed as needed. In addition, when the first anti-rotation recess 616 of the mounting portion 601 is set to a structure used when the working machine 1 is used, shaking during operation can be suppressed.

[0263] Although the present invention has been described above by taking the embodiment as an example, the present invention is not limited to the embodiment. Various modifications can be made to the matters specifically described in the embodiment within the scope described in the claims.

[0264] The concave-convex structure illustrated in the embodiment may be appropriately reversed in the relationship between the concave and convex. 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 engaged 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 engaged with the concave portion.

[0265] The number of the outer peripheral side protrusions 91 or the stop blocks 120 of the final ring gear 90, the number of screws 44, the number of screws 133, the number of levels of set tightening torque, the number of types of installable angles of the sub-handle 600 relative to the working machine 1, the number of first anti-rotation recesses 616 and the second anti-rotation recesses 617, etc., which are exemplified as specific quantities in the embodiment, do not limit the scope of the invention in any way and can be changed arbitrarily to meet the required specifications.

[0266] Explanation of symbols

[0267] 1: Operating machine

[0268] 4: Transfer / output structure

[0269] 5: Delivery Department

[0270] 6: Output switching unit

[0271] 7: Output section

[0272] 10: Shell

[0273] 11: Motor housing

[0274] 12: Handle part

[0275] 13: Battery assembly equipment

[0276] 15: Tail hood

[0277] 17: Trigger switch

[0278] 19: Forward and reverse switch

[0279] 20: Top Tools

[0280] 21: Speed ​​Shift Button

[0281] 23: Control board

[0282] 25: Battery Pack

[0283] 27: Screw

[0284] 30: Motor

[0285] 31: Motor shaft

[0286] 33: Ball bearing

[0287] 35: Fan

[0288] 37: Sensor substrate

[0289] 40: Motor spacer

[0290] 41: Bearing retaining part

[0291] 42: Gear Department

[0292] 43: Screw insertion hole

[0293] 45: Screw sleeve

[0294] 50: Transmission mechanism (reduction mechanism)

[0295] 51: First planetary gear

[0296] 53: Needle roller bearing

[0297] 55: First planet carrier

[0298] 57: Sliding ring gear

[0299] 58: Groove

[0300] 60: Back shell

[0301] 61: Cylindrical part

[0302] 62: Threaded boss

[0303] 63: Guide convex part

[0304] 64: Guide hole

[0305] 65: Spring retaining hole

[0306] 66: Flange

[0307] 67: Through hole

[0308] 68: Left grease cover

[0309] 69: Right grease cover

[0310] 71: Speed ​​change arm

[0311] 75: Speed ​​Claw

[0312] 81: Second planetary gear

[0313] 85: Second planet carrier

[0314] 87: Final Planetary Gear

[0315] 90: Final Ring Gear

[0316] 91: Outer circumferential convex part

[0317] 92: Cylindrical part

[0318] 93: Flange

[0319] 94: Gear Department

[0320] 95: Front surface convex part

[0321] 96: Front surface concavity

[0322] 101: Final Planetary Holder

[0323] 103: Roller

[0324] 105: Spline hub

[0325] 110: Lock ring

[0326] 115: Hub washer

[0327] 117: Stop spring (force applying component)

[0328] 120: Stop block

[0329] 121: Base

[0330] 122: Spring retaining part

[0331] 123: locking convex part (protrusion)

[0332] 124: Wide convex part

[0333] 131: Clutch pin

[0334] 133: Screw

[0335] 135: Spring washer

[0336] 140: Gearbox

[0337] 141: Rear cylindrical part

[0338] 142: Front wall

[0339] 143: Through hole

[0340] 144: Stopper

[0341] 145: Through hole

[0342] 146: Central through hole

[0343] 147: Through hole

[0344] 148: Anti-rotation part convex part

[0345] 149: Anti-rotation part convex part

[0346] 150: Front cylindrical part

[0347] 151: Screw hole

[0348] 152: Stopper insertion groove, stopper insertion hole

[0349] 161: Pin sleeve

[0350] 165: Thrust plate

[0351] 210: Rear stop cam ring

[0352] 211: Flat part

[0353] 212: Outer peripheral side inclined portion

[0354] 213: Outer circumferential flat portion

[0355] 214: Inner circumference side inclined portion

[0356] 215: Inner circumference flat part

[0357] 218: Anti-rotation recess

[0358] 219: Anti-rotation recess

[0359] 230: Front stop cam ring

[0360] 232: Outer peripheral protrusion

[0361] 234: Inner circumference protrusion

[0362] 235: Locking protrusion

[0363] 250: Clutch spring

[0364] 260: Nut

[0365] 261: Threaded part

[0366] 262: Spring stop hole

[0367] 263: Incision

[0368] 280: Ratchet cam ring

[0369] 282: Outer peripheral protrusion

[0370] 284: Inner circumference protrusion

[0371] 285: Anti-rotation protrusion

[0372] 286: Inclined part

[0373] 287: Inclined part

[0374] 288: Small protrusion

[0375] 300: Clutch dial

[0376] 301: Threaded part

[0377] 302: Locking recess

[0378] 304: Inner circumferential side concave portion

[0379] 305: Peripheral side hole part

[0380] 306: Cylindrical part

[0381] 307: Front wall

[0382] 308: Leaf spring mounting part

[0383] 331: Leaf spring

[0384] 335: Ball bearing (bearing)

[0385] 340: Front shell

[0386] 341: Large diameter cylinder

[0387] 342: Small diameter cylinder

[0388] 343: Connecting the Face

[0389] 344: Incision

[0390] 345: Threaded boss

[0391] 346: Screw hole

[0392] 347: Screw hole

[0393] 348: Bearing retaining part

[0394] 349: Anti-rotation protrusion (rotation limiting portion)

[0395] 350: Stop protrusion

[0396] 351: Locking recess

[0397] 360: Ratchet Spring

[0398] 370: Clutch hub

[0399] 371: Annular part

[0400] 372: Outer protrusion

[0401] 373: Locking convex part

[0402] 374: Inclined part

[0403] 391: Thrust bearing

[0404] 395: Bearing washer

[0405] 410: Rear ratchet

[0406] 411: Concavoconvex part (vibration generating shape part)

[0407] 412: locking convex part

[0408] 413: Inclined part

[0409] 431: Spring

[0410] 435: Ratchet washer

[0411] 440: Front ratchet

[0412] 441: convex portion (vibration generating shape portion)

[0413] 461: Ball bearings

[0414] 470: Spindle

[0415] 481: O-ring

[0416] 483: Retaining ring

[0417] 485: Bearing cover

[0418] 487: Through hole

[0419] 489: Screw

[0420] 495: Left screw

[0421] 500: Chuck

[0422] 600: Secondary handle

[0423] 601: Installation Department

[0424] 602: First shaft

[0425] 603: Second shaft

[0426] 604: Handle

[0427] 605: Knob bolt

[0428] 606: Pin layer through hole

[0429] 607: Pin

[0430] 608: retaining ring

[0431] 609: O-ring

[0432] 610: Head

[0433] 611: Axis

[0434] 612: First cylindrical part

[0435] 613: Second cylindrical portion

[0436] 614: Gap

[0437] 615: Ring

[0438] 616: First anti-rotation recess

[0439] 617: Second anti-rotation recess

[0440] 618: Large diameter part

[0441] 619: Trails

[0442] 620: Pin insertion slot

[0443] 621: O-ring embedded groove

[0444] 622: External thread

[0445] 623: Nut

[0446] 624: Head holding part

[0447] 625: Flange

[0448] 626: Shaft insertion part

[0449] 627: Shaft insertion part

[0450] 628: Expansion section

Claims

1. A working machine, characterized in that: include: motor; An output portion, comprising a top tool holding portion and a bearing portion for supporting the top tool holding portion, and located on one side of the motor in the axial direction of the motor; A transmission part, which transmits the driving force of the motor to the top tool holding part, is detachably assembled to the output part from the other side in the axial direction and is located on one side of the motor in the axial direction; as well as an output switching unit that switches the output of the output unit and is sandwiched between the output unit and the transmission unit, If the transmission unit is removed from the output unit, the output switching unit can be removed from the output unit to the other side in the axial direction.

2. The working machine according to claim 1, characterized in that: comprising a fixing portion, wherein the fixing portion fixes the output portion and the transmission portion, When the fixing by the fixing portion is released, the transmission portion can be removed from the output portion.

3. The working machine according to claim 2, characterized in that: The transmission part has: a transmission mechanism, including gears; and The transmission part housing accommodates the transmission mechanism. A transmission unit housing side mounting portion is provided on a wall portion on one side in the axial direction of the transmission unit housing, and the transmission unit housing side mounting portion is used to mount the fixing portion to the output portion from the other side in the axial direction.

4. The working machine according to claim 3, characterized in that: The output part has an output part housing, and the output part housing holds the top tool holding part and the bearing part. An output portion housing side mounting portion is provided on the other side of the output portion housing in the axial direction, and the fixing portion is mounted on the output portion housing side mounting portion.

5. The working machine according to claim 2, characterized in that: In the axial direction, at least a portion of the fixing portion overlaps with an existing range of the output switching portion.

6. The working machine according to any one of claims 1 to 5, characterized in that: The top tool holding portion has: a main shaft connected to the transmission part; and A chuck holds a top tool and rotates integrally with the spindle.

7. The working machine according to claim 6, characterized in that: The output switching portion is located on the other side of the chuck in the axial direction, and movement to one side in the axial direction is restricted.

8. The working machine according to claim 7, characterized in that: If the transmission portion is removed from the output portion, the output switching portion can be removed from the output portion to the other side in the axial direction while the spindle and the chuck are fixed.

9. The working machine according to claim 6, characterized in that: A clutch mechanism is included, wherein the clutch mechanism cuts off the rotation transmission from the transmission part to the main shaft at a predetermined torque, The output switching unit includes a switching operation unit capable of switching the predetermined torque.

10. The working machine according to claim 4, characterized in that: The fixing part is a screw, The transmission part housing side mounting portion is a through hole for the screw to pass through. The output housing side mounting portion is a screw hole for the screw to be screwed.

11. A working machine, characterized in that: include: motor; An output portion, comprising a top tool holding portion and a bearing portion for supporting the top tool holding portion, and located on one side of the motor in the axial direction of the motor; A transmission part, which transmits the driving force of the motor to the top tool holding part, is detachably assembled to the output part from the other side in the axial direction and is located on one side of the motor in the axial direction; as well as an output switching unit that switches the output of the output unit and is sandwiched between the output unit and the transmission unit, The output unit is configured to support a main shaft connected to the transmission unit.

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