JP2020075330A - Electric power tool - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vibration switching means including a vibration switching member, and thus an electric tool having a compact size as a whole. An electric vibration driver drill, which is an example of an electric tool, has a motor, a spindle 55 that can be rotated by the motor, a first vibration cam 152 fixed to the spindle 55, and a first vibration cam 152 inward. The gear housing 52 to be arranged, the second vibration cam 154 arranged inside the gear housing 52 and capable of rubbing against the first vibration cam 152, and the rotation of the second vibration cam 154 with respect to the gear housing 52. It has three vibration switching levers 172 for switching whether or not to enable, and a plurality of (two each for a total of six) coil springs 182 for each vibration switching lever that urge each vibration switching lever 172. [Selection diagram] FIG. 27

Description

  The present invention relates to a power tool such as an electric vibration driver drill or an electric vibration drill.

As disclosed in JP-A-2017-100259 (Patent Document 1), in a vibration driver drill, a vibration switching lever 66 as a vibration switching member for switching presence / absence of vibration is provided from the front end of the small diameter portion 39 of the second gear case 39. It is known that each of the slits 64 is formed in a pair of slits 64 formed along the axial direction.
Each vibration switching lever 66 can move back and forth within the slit 64, and is biased forward by one coil spring 65. A cam ring 84 of a mode change ring 82 is arranged in front of each vibration switching lever 66, and when the mode change ring 82 is rotated to a position corresponding to the vibration mode, each vibration switching lever 66 moves the cam of the cam ring 84. It moves into the recess and moves forward, and engages with the claw 60 of the second cam 56 of the vibration mechanism 54 arranged between the vibration switching levers 66. The second cam 56 is made unrotatable around the shaft by the engagement of the respective vibration switching levers 66, and when the first cam 55 that rotates integrally with the spindle 5 comes into contact, the first cam 55 and the second cam 56 (vibration mechanism 54). Produces a vibration.

JP, 2017-100259, A

  The main object of the present invention is to provide a vibration switching means including a vibration switching member, and further, an electric tool which is compact as a whole.

In order to achieve the above object, the invention according to claim 1 provides a motor, a spindle rotatable by the motor, a first vibration cam fixed to the spindle, and the first vibration cam inward. A housing to be arranged, a second vibration cam that is arranged inside the housing and can rub against the first vibration cam, and a vibration switching that switches whether the second vibration cam can rotate with respect to the housing. A member and a plurality of biasing members for biasing the vibration switching member.
According to a second aspect of the invention, in the above invention, three or more of the biasing members are provided and are arranged in the circumferential direction.
According to a third aspect of the present invention, in the above invention, a plurality of the vibration switching members are provided and are arranged in the circumferential direction.
According to a fourth aspect of the present invention, in the above invention, the second vibration cam has a pawl, the vibration switching member has a vibration switching pawl, and the pawl has the vibration switching pawl. It is characterized in that it prevents the rotation of the second vibration cam by being applied.

  According to the present invention, there is provided a vibration switching means including a vibration switching member, and by extension, an electric tool which is compact as a whole.

It is a perspective view of a driver drill concerning the present invention. It is a right view of FIG. It is a front view of FIG. It is a top view of FIG. FIG. 3 is a cross-sectional view of KAZAMADO-KAZAMADO of FIG. 2. It is a BB-BB sectional view of FIG. It is a GRIP1-GRIP1 sectional view of FIG. It is a GRIP2-GRIP2 sectional view of FIG. It is a GRIP3-GRIP3 sectional view of FIG. It is a right view of the gear assembly in the electric vibration driver drill of FIG. It is a front view of FIG. FIG. 11 is a rear view of FIG. 10. It is a perspective view which decomposed | disassembled only the front part of FIG. FIG. 11 is an exploded perspective view of a part of FIG. 10. FIG. 11 is an exploded perspective view of another part of FIG. 10. FIG. 12 is a FRONT-FRONT sectional view of FIG. 11. FIG. 12 is a cross-sectional view taken along the line TOP-TOP of FIG. 11. It is a NEJI1-NEJI1 sectional view of FIG. FIG. 17 is a QQ sectional view of FIG. 16. FIG. 17 is a sectional view taken along line AA of FIG. 16. It is a CAM-CAM sectional view of FIG. FIG. 17 is a sectional view taken along line BB of FIG. 16. It is CC sectional drawing of FIG. FIG. 17 is a sectional view taken along line TT of FIG. 16. FIG. 25 is a sectional view taken along line GG of FIG. 24. FIG. 17 is a sectional view taken along line DD of FIG. 16. It is a VV sectional view of FIG. 16A is a sectional view taken along line ZZ of FIG. 16, and FIG. 16B is a sectional view taken along line AA-AA of FIG. FIG. 17 is an S-S sectional view (during rotation) of FIG. 16. FIG. 17 is a cross-sectional view taken along line S-S of FIG. 16 (when stopped). FIG. 17 is a sectional view taken along line EE in FIG. 16. FIG. 17 is a sectional view taken along line F-F in FIG. 16. FIG. 17 is a sectional view taken along line JJ of FIG. 16. FIG. 17 is a sectional view taken along line HH of FIG. 16. FIG. 17 is a sectional view taken along line L-L in FIG. 16. It is a figure when a part of outline is removed in FIG. FIG. 17 is a view similar to FIG. 16 in the vibration mode and the high speed mode. It is WW sectional drawing of FIG. FIG. 37 is a diagram in a mode other than the clutch mode in which some internal mechanisms are removed in FIG. 36. FIG. 11 is a view similar to FIG. 10 in the clutch mode. FIG. 18 is a view similar to FIG. 17 in the clutch mode and the high speed mode. FIG. 40 is a view similar to FIG. 39 in the clutch mode.

Hereinafter, embodiments of the present invention and modifications thereof will be described with reference to the drawings as appropriate.
The front, rear, upper, lower, left, and right in the form and the modified example are determined for convenience of description, and may change depending on at least one of the working situation and the state of the moving member.
The present invention is not limited to the following modes and modifications.

FIG. 1 is a perspective view of an electric vibration driver drill 1 which is an example of an electric tool. FIG. 2 is a right side view of the electric vibration driver drill 1. FIG. 3 is a front view of the electric vibration driver drill 1. FIG. 4 is a top view of the electric vibration driver drill 1. FIG. 5 is a cross-sectional view of KAZAMADO-KAZAMADO of FIG. FIG. 6 is a sectional view taken along line BB-BB in FIG. FIG. 7 is a sectional view of GRIP1-GRIP1 in FIG. FIG. 8 is a cross-sectional view of GRIP2-GRIP2 in FIG. FIG. 9 is a cross-sectional view of GRIP3-GRIP3 of FIG.
The electric vibration driver drill 1 has a housing 2 forming an outer shell thereof.
The electric vibration driver drill 1 has a tubular main body 4 having a central axis in the front-rear direction, and a grip portion 6 formed so as to project downward from a lower portion of the main body 4. In FIG. 2, the right is the front and the upper is the top, and in FIG. 4, the upper is the left and the right is the front.
The grip portion 6 is a portion to be gripped by the user, and a trigger-type switch lever 8 that can be pulled by a user with a fingertip is provided at an upper end portion of the grip portion 6. The switch lever 8 projects from the switch body 9 (see FIGS. 7 and 8).

As shown in FIGS. 5 and 6, a motor 10 is housed in the rear portion of the main body portion 4 of the electric vibration driver drill 1. A gear assembly 12 is arranged on the front side of the motor 10. A chuck 14 capable of gripping a bit (tip tool) is provided on the front side of the gear assembly 12.
The motor 10 is a drive source of the electric vibration driver drill 1. The rotation of the motor 10 is decelerated by the gear assembly 12 and transmitted to the chuck 14 and the bit. Incidentally, in FIG. 6, a part of the motor 10 is omitted.

  The housing 2 includes a resin main body housing 20 that holds the motor 10, the switch main body 9, and the like, and a resin rear cover 22 that covers the rear of the motor 10.

The main body housing 20 includes the outer contour of the grip portion 6.
The main body housing 20 has a left main body housing 20a and a right main body housing 20b that are half-divided. The left main body housing 20a has a plurality of screw boss portions, and the right main body housing 20b has screw holes corresponding to the screw boss portions. The left main body housing 20a and the right main body housing 20b are aligned with each other by the screws 24 in the left-right direction that enter each set of screw holes and screw boss portions.
The respective rear portions of the main body portion 4 of the left main body housing 20a and the right main body housing 20b are combined with each other to form an opening, and the rear cover 22 is fixed to the opening by a plurality of screws 25 extending in the front-rear direction. There is. The screws 25 are arranged vertically (only the upper screw 25 is shown), and the rear cover 22 is securely fixed.
A plurality of intake ports 20c extending in the up-and-down direction are opened in front and rear at upper and lower sides of the rear end portions of the left main body housing 20a and the right main body housing 20b. That is, the plurality of intake ports 20c are formed in a continuous slit shape arranged along the front adjacent portion of the rear cover 22. In addition, a plurality of exhaust ports 22a extending in the front-rear direction are formed in a side portion of the rear cover 22 behind the intake ports 20c so as to be vertically aligned.

As shown in FIGS. 2 and 3, a forward / reverse switching lever 26, which is a switch for switching the rotation direction of the motor 10, is provided behind the switch lever 8 in the left and right direction in the boundary region between the main body portion 4 and the grip portion 6. It is provided to do.
Further, on the upper side of the switch lever 8 and in front of the forward / reverse switching lever 26, a plurality of (two) lights 28 capable of illuminating the front are provided side by side. Each light 28 is here an LED.

A lower end portion of the grip portion 6 serves as a battery mounting portion 30 that spreads outward with respect to an upper portion thereof, and a battery 32 is detachably held below the battery mounting portion 30 by a battery button 32a. The battery 32 is a lithium-ion battery and includes a plurality of cells (not shown). The cell has a columnar shape that is long in the axial direction and faces the left-right direction.
A display unit 33 that displays the state of the electronic gear by the lighting mode of a plurality of lamps is provided on the upper front portion of the battery mounting unit 30 (the front upper surface portion of the lower portion where the grip portion 6 is widened).
The battery 32 is mounted by sliding the battery 32 from the front to the rear of the battery mounting portion 30 with the battery terminal portion facing upward and the raised portion 32b facing upward. When mounted, the rear portion of the raised portion 32b contacts the front portion of the battery mounting portion 30, and the battery terminal portion contacts the battery mounting terminal portion of the battery mounting portion 30. In addition, the battery claw that is urged upward by the elastic member at the time of mounting and projects from the upper surface of the other part of the battery 32 enters the upwardly recessed battery mounting recess provided in the lower front portion of the battery mounting portion 30. On the other hand, when the battery 32 is removed, the battery button 32a connected to the elastic member of the battery claw is operated, and the battery 32 is slid forward while the battery claw is disengaged from the battery mounting recess.
A hook 34 and a bit holder 35 are arranged on the battery mounting portion 30, respectively. The hook 34 and the bit holder 35 can be attached to the left portion or the right portion of the battery attachment portion 30 with a screw 36. The hook 34 includes a U hook portion 34a having a "U" shape in a front view, a first loop hook portion 34b having a "Ω" shape in a side view, a portion along the first loop hook portion 34b, and a loop shape portion in a top view. And a second loop hook portion 34c having. The parallel front end portion of the first loop hook portion 34b and both end portions of the second loop hook portion 34c are held in a tubular portion 34d formed in the upper end portion of the U hook portion 34a and having the axial direction as the front-back direction. ing. The bit holder 35 detachably holds a plurality of (two) bits 35a by sliding forward. The bit 35a can be attached to the bit holder 35 by sliding it backward.
As shown in FIGS. 2 and 9, a control circuit board 38 of a controller that controls the motor is held in the battery mounting portion 30. The control circuit board 38 has a cylindrical capacitor 38a protruding upward from other portions and a microcomputer. The control circuit board 38 is electrically connected to the motor 10 by power lead wires and signal lead wires (not shown). The control circuit board 38 is also electrically connected to the battery mounting terminal portion of the battery mounting portion 30.

As shown in FIGS. 5 and 6, the motor 10 is a brushless motor, and includes a cylindrical stator 40 and a rotor 41 arranged inside the stator 40.
The rotor 41 includes a cylindrical motor shaft extending in the front-rear direction, a pinion 43 (FIG. 6) integrated with a front end portion of the motor shaft, a cylindrical rotor core arranged around a central portion of the motor shaft, A permanent magnet disposed in the rotor core.
A cooling fan 44 is attached to the rear of the motor shaft via a metal insert bush (not shown). The fan 44 is a centrifugal fan. Since the insert bush is press-fitted, the fixing force of the fan 44 with respect to the motor shaft is high.
Each exhaust port 22a is located outside the fan 44 in the radial direction.
On the rear side of the fan 44 and on the inner surface of the rear portion of the rear cover 22, a motor rear bearing that rotatably supports the motor shaft rear end portion is held.
The stator 40 includes a stator core 45 having a cylindrical portion whose axial direction is the front-rear direction, and a plurality of teeth 45a which respectively protrude inward in the radial direction from the inner surface thereof, and ring-shaped stators 45 attached to the front and rear of the stator core 45, respectively. Front insulating member 46A and rear insulating member 46B, a coil 47 wound around each tooth 45a via the front insulating member 46A and rear insulating member 46B, a sensor substrate 48 attached to the front side of the front insulating member 46A, and its front side. And a ring-shaped synthetic resin sheet metal member 49 including a plurality of arc-shaped sheet metals.
The sensor board 48 detects the rotational position of the rotor 41 (permanent magnet) and transmits it to the control circuit board 38.
The sheet metal of the sheet metal member 49 electrically connects the coils 47 to each other in a predetermined manner, and at the same time, connects the power source lead wire to the control circuit board 38.

As shown in FIGS. 10 to 42, the gear assembly 12 has, as its outer shell, a cylindrical gear case 50, and a plate-shaped (dish-shaped) motor bracket 51 arranged on the rear side of the rear end of the gear case 50. A metal gear housing 52 having a double inner and outer cylindrical shape arranged on the front side of the gear case 50, and arranged on the front side of the gear housing 52, exposed at the upper front portion of the housing 2, and mounted on the housing 2. It has a clutch ring 53 as a clutch switching ring, and a mode switching ring 54 on the front side thereof, which is externally mounted on the housing 2 similarly to the clutch ring 53.
A spindle 55 is arranged radially inward of the front part of the outer contour of the gear assembly 12 along the central axis of the gear assembly 12. The tip of the spindle 55 projects forward from the outer contour of the gear assembly 12.
The spindle 55 is a columnar member having the axial direction as the front-rear direction, and has a spindle flange 55a that expands radially outward at the center in the front-rear direction and a diameter that is smaller behind the spindle flange 55a than at the front thereof. A front step portion 55b, a middle step portion 55c, a rear step portion 55d, a clip groove 55e circumferentially formed on the front side of the middle step portion 55c, and a spindle that extends forward and backward at the center of the front portion and opens at the front end. The hole 55f is provided. The spindle hole 55f is a bolt hole having a thread groove. A male screw portion (not shown) is formed on the outer surface of the front end portion of the spindle 55 radially outward of the spindle hole 55f.
The chuck 14 has a female screw portion corresponding to the male screw portion of the spindle 55 (not shown). The chuck 14 is fixed to the spindle 55 by receiving a male screw portion of the spindle 55 in a female screw portion and inserting a bolt (not shown) in the spindle hole 55f. At least one of the spindle 55 and the chuck 14 can be regarded as an output shaft.

The gear case 50 has a cylindrical gear case base 50a, and a screw having a screw hole at the center of each of the projecting pieces radially outwardly projecting to the upper right / lower right / upper left / lower left of the gear case base 50a. The hole 50b is formed. Similarly, screw holes 51b and screw holes 52b are formed in the bottom of the motor bracket base 51a of the motor bracket 51 and the rear part of the outer cylinder 52a of the gear housing 52. The screw hole portion 51b projects radially outward and forward. The screw hole portion 52b projects radially outward. The screw 56 common to the upper right screw holes 50b and 51b or the screw hole 52b is passed through, and the same applies to the lower right, upper left, and lower left. By thus tightening the gear case 50 and the gear housing 52 (and the motor bracket 51) together by the common connecting means, the adhesion between them is improved, the internal mechanism is protected, and grease or the like is attached to the internal mechanism. When applied, it is possible to prevent leakage of grease and the like. Further, the gear assembly 12 becomes compact as compared with the case where the connecting member for the motor bracket 51 and the gear case 50 and the connecting member for the gear case 50 and the gear housing 52 are separately provided.
The front outer surface of the outer cylindrical portion 52a of the gear housing 52 is circumferentially adjacent to the screw hole portion 52b (below the upper screw hole portion 52b and above the lower screw hole portion 52b). A side handle mounting portion 52c, which is a front-rear recess for receiving a "C" -shaped handle side mounting portion of a side handle (not shown), is formed. By inserting the forked ends of the handle-side attachment portions into the pair of side handle attachment portions 52c on the right side or the left side, the side handles extending in the left-right direction are attached. Even if the side handle tries to rotate around the handle-side mounting portion, the screw hole portion 52b protruding outward in the circumferential direction blocks the handle-side mounting portion, so that the rotation is prevented, and the side handle is stably mounted. Maintained.

The gear assembly 12 has a screw hole portion 57 arranged radially outward of each screw hole portion 52b of the gear housing 52, and a screw 58 that is inserted into a screw hole formed in an opening portion of the main body portion 20 of the main body housing 20. It is attached to the front of the opening of the main body housing 20. The screw holes 57 have a narrower left-right space than the lower two in the left-right direction. Therefore, the arrangement of the screw hole portions 57 is adapted to the shape of the cylindrical main body portion 4 in which the grip portion 6 extends downward, which contributes to downsizing in the left-right direction.
As shown in FIG. 6, a rib 20d that protrudes radially inward is provided on the inner surface of the opening of the main body housing 20. The rib 20d is on the side surface of the gear case base 50a and is adjacent to the rear side of the enlarged diameter portion with respect to the gear housing 52. The rib 20d receives a reaction force of stress deformation generated in the gear case 50 by the operation of an internal mechanism of the gear assembly 12 (a middle planetary gear mechanism 70 and the like described later). Therefore, the gear assembly 12 is securely held.
Further, on the left and right of the rear portion of the lower surface of the outer tubular portion 52a of the gear housing 52, there are provided projections 59 that project downward and outward in the left-right direction. Each projection 59 is locked to the inner surface of the main body housing 20 to prevent the gear assembly 12 and the main body housing 20 from being separated from each other.
The front portion, the side portion, and the upper portion of the gear housing 52 are exposed to be a part of the outer shell of the main body portion 4, and the gear housing 52 is a part of the housing 2.

A motor front bearing (not shown) that rotatably supports the pinion 43 (see FIG. 6) at the motor shaft front end is placed in the central hole 51c of the motor bracket 51. In the motor bracket 51, as shown in FIG. 35 in particular, a plurality of (seven) projections 51d protruding radially outward from the outer surface of the cylindrical portion of the motor bracket base portion 51a are formed on the inner surface of the rear end portion of the gear case base portion 50a. The rotation is stopped by entering the formed inner groove 50c that extends in the front-rear direction and is recessed radially outward.
At least one of the motor bracket 51, the clutch ring 53, the mode switching ring 54, and the spindle 55 may be regarded as not a constituent element of the gear assembly 12, and the motor bracket 51 is a constituent element of the motor 10. You may be caught. Further, at least one of the chuck 14, the motor front bearing, and the pinion 43 may be regarded as a component of the gear assembly 12.

  Further, the gear assembly 12 has a three-stage planetary gear mechanism inside, and decelerates the rotation of the motor shaft and transmits it to the spindle 55. That is, the gear assembly 12 includes a rear planetary gear mechanism 60 (first stage reduction mechanism), a middle planetary gear mechanism 70 (second stage reduction mechanism), and a front planetary gear mechanism 80 (third stage reduction mechanism). Have.

As shown in FIGS. 33 and 34, the rear planetary gear mechanism 60 includes a plurality (five) of internal gears 62 fixed in the gear case 50 and external teeth meshing with the internal teeth of the internal gears 62. And a carrier 66 that rotatably supports each planet gear 64 via a needle bearing 65.
The internal gear 62 has a plurality of (four) projections 62b protruding radially outward from a ring-shaped inner tooth portion 62a, and a plurality of slits 51e formed in the cylindrical surface of the motor bracket base 51a and extending in the front-rear direction. , And the inner groove 50d formed on the inner surface of the rear end portion of the gear case base 50a and extending in the front-rear direction and dented radially outward is prevented from rotating.
Each planetary gear 64 meshes with the pinion 43 (see FIG. 6) of the motor shaft.
The carrier 66 has five pins 66b protruding rearward from the rear surface of the disk-shaped portion 66a having a hole in the center so as to be equally spaced in the circumferential direction, and one planet gear 64 is provided for each pin 66b. And the needle bearing 65 is supported. Further, the carrier 66 has an external gear 66c that projects forward from the center of the front surface of the disk-shaped portion 66a in a cylindrical shape. Further, meshing teeth 66d are provided on the outer surface of the front portion of the disc-shaped portion 66a.
Since the planetary gear 64 is supported by the needle bearing 65, the supporting strength is higher than that of the ball bearing. Therefore, even if the planetary gear 64 is thinned in the axial direction (front-back direction), it is possible to secure the same strength as that of the ball bearing, and the planetary gear 64 or the rear planetary gear mechanism 60, and thus the electric vibration driver drill 1 are moved forward and backward. More compact in direction.
A washer 68 is arranged between each planet gear 64 and the motor bracket 51.

As shown in FIGS. 32 and 33, the middle planetary gear mechanism 70 includes an internal gear 72, a plurality of (five) planetary gears 74 having external teeth meshing with internal teeth of the internal gear 72, and each planetary gear 74. It has a carrier 76 that rotatably supports the planet gears 74.
A plurality of outer teeth 72b, which protrude in the radial direction and extend in the front-rear direction, are provided at predetermined intervals in the circumferential direction at the front portion of the outer surface of the ring-shaped inner tooth portion 72a of the internal gear 72. A coupling groove 72c extending in the circumferential direction is provided on the rear portion of the outer surface of the. Further, a meshing tooth 72d capable of meshing with the meshing tooth 66d of the first stage carrier 66 is provided on the rear side opening portion of the internal gear 72.
Each planetary gear 74 meshes with the external gear 66c of the first-stage carrier 66.
The carrier 76 has five pins 76b protruding rearward from the rear surface of the disk-shaped portion 76a having a hole in the center, and one planet gear 74 is supported by each pin 76b. Further, the carrier 76 has an external gear 76c that protrudes forward in a cylindrical shape from the center of the front surface of the disk-shaped portion 76a.

As shown in FIG. 32, a coupling ring 77 held at the rear of the gear housing 52 is arranged outside and on the front side of the internal gear 72. Inner teeth 77b protruding radially inward and extending in the front-rear direction are provided on the inner peripheral surface of the ring-shaped connecting ring base 77a of the connecting ring 77 in the same number as the outer teeth 72b of the internal gear 72. Further, on the outer peripheral surface of the coupling ring base portion 77a, a plurality (six) of protrusions 77c protruding outward and extending in the front-rear direction are provided at predetermined intervals in the circumferential direction. Each outer tooth 72b of the internal gear 72 can enter between any inner teeth 77b of the coupling ring 77.
The coupling ring 77 includes a plurality of arcuate ribs 50e formed at the front end of the gear case base 50a at equal intervals in the circumferential direction, and the rear of the outer cylindrical portion 52a of the gear housing 52. The rotation is stopped by entering the inner groove 52d formed on the inner surface of the end portion and extending in the front-rear direction and recessed radially outward. Further, on the radially outer surface of the lower arc-shaped rib 50e, a protruding portion 50f that radially outwardly projects is formed. The protruding portion 50f is in an inner groove 52e formed in the inner surface of the rear end portion of the outer cylindrical portion 52a of the gear housing 52, extending in the front-rear direction, and recessed radially outward.

On the other hand, as shown in FIG. 33, a speed switching ring 78 is arranged outside the rear part of the internal gear 72. At the upper part of the ring-shaped speed switching ring base 78a of the speed switching ring 78, a connecting piece 78b protrudes rearward and upward in a side view "L" shape, and is formed on the left, right, and lower portions of the speed switching ring base 78a. Have projecting pieces 78c projecting radially outward and rearward, respectively.
As shown in FIG. 34, the gear case 50 is provided with a slit 50g that goes forward from the upper rear portion, and the slit 50g includes the lower end portion of the upward protruding portion of the connecting piece 78b. The upper part of the upward projecting portion of the connecting piece 78b is provided at the lower part of the speed switching lever 79 (see FIGS. 1, 2 and 4) slidably provided in the upper part of the housing 2 so that the coil springs (elastic body) are arranged in the front and rear. , Not shown). The front portion of the speed switching lever 79 is in a hole portion 52f having a hole formed so as to extend forward from the rear end in the upper portion of the outer tubular portion 52a of the gear housing 52. Upper screw hole portions 57 are arranged on both left and right sides of the hole portion 52f.
As shown also in FIG. 33, a guide groove 50h in the front-rear direction corresponding to each protrusion 78c of the speed switching ring 78 is provided on the inner surface of the gear case base 50a, and each guide groove 50h corresponds to each guide groove 50h. A protrusion 78c is inserted and the speed switching ring 78 is supported so as to move only in the front-rear direction.
In addition, a total of two pins 78d are provided from the outside in the radial direction of the left and right protrusions 78c to the inside. The outer head of each pin 78d abuts the outer surface of each of the left and right protrusions 78c, and the inner tip of each pin 78d, which is narrower than the head of each pin 78d, projects radially inward from the inner surface of each protrusion 78c to form an internal gear. It is in the coupling groove 72c of 72.

When the speed switching lever 79 is moved to the front, the speed switching ring 78 moves forward through the connecting piece 78b, and the internal gear 72 keeps meshing with each planetary gear 74 through each pin 78d or coupling groove 72c. Move forward. Then, the outer teeth 72b enter between the inner teeth 77b of the coupling ring 77, the circumferential rotation of the internal gear 72 is restricted, and the planetary gears 74 circulate around the fixed internal gear 72. The rotation reduced in speed from the rotation of the first-stage external gear 66c is transmitted to the external gear 76c of the carrier 76. That is, when the speed switching lever 79 is set to the front, a low speed mode in which deceleration by the second intermediate planetary gear mechanism 70 functions is achieved.
On the other hand, as shown in FIGS. 37 and 41, when the speed switching lever 79 (see FIGS. 1, 2 and 4) is moved backward, the speed switching ring 78 similarly moves rearward so that the internal gear 72 moves. It moves rearward while maintaining meshing with each planetary gear 74. Then, the external teeth 72b come out from between the internal teeth 77b of the coupling ring 77, and the rotation restriction of the internal gear 72 in the circumferential direction is released, so that the internal gear 72 of the meshing teeth 66d of the first stage carrier 66 is released. The meshing teeth 72d mesh with each other, and both the internal gear 72 that is not fixed in the circumferential direction and the first-stage carrier 66 rotate, and the rotation equivalent to the rotation of the external gear 66c is transmitted to the external gear 76c. That is, when the speed switching lever 79 is moved backward, the high speed mode in which the deceleration by the second-stage middle planetary gear mechanism 70 is canceled.
A rib 78e that extends in the front-rear direction and projects downward is provided at the center of the lower surface of the connecting piece 78b in the left-right direction. Therefore, the rigidity of the connecting piece 78b is ensured, the bending is prevented, and the position of the internal gear 72 after the movement by the speed switching ring 78 is stabilized. The rib 78e is in a groove 51f that extends in the front-rear direction and is recessed downward on the upper surface of the motor bracket base portion 51a. The slit 50g of the gear case 50 is located above the groove 51f.

As shown in FIG. 30 and FIG. 31, the front planetary gear mechanism 80 includes an internal gear 82 rotatably provided in the gear housing 52 in a circumferential direction and external teeth meshing with internal teeth of the internal gear 82. It has a plurality of (six) planetary gears 84 and a carrier 86 that rotatably supports each planetary gear 84.
A plurality of (six) cam protrusions 82b protruding forward are provided on the front surface of the cylindrical inner tooth portion 82a of the internal gear 82 at predetermined intervals in the circumferential direction. Further, a plurality of (six) protrusions 82c that protrude outward in the radial direction are provided on the outer surface of the inner tooth portion 82a. Each protruding portion 82c is arranged in the central portion between the cam protrusions 82b in the inner tooth portion 82a.
Each planet gear 84 meshes with the external gear 76c of the second-stage carrier 76.
The carrier 86 has a plurality of (six) pins 86b protruding rearward from the rear surface of the disk-shaped portion 86a having a hole in the center, and one planet gear 84 is supported by each pin 86b. Further, the carrier 86 has a plurality of (four) projections 86c that project in a semi-cylindrical shape from the center of the front surface of the disk-shaped portion 86a and are arranged in the circumferential direction (see FIG. 14, FIG. 28A, etc.). ).

As shown in FIGS. 19 and 20, the clutch ring 53 is arranged radially outward of the inner tubular portion 52g of the gear housing 52. The inner cylinder portion 52g has a cylindrical shape with a smaller diameter than the outer cylinder portion 52a. The front end of the inner tubular portion 52g is located in front of the front end of the outer tubular portion 52a. The clutch ring 53 has a ring-shaped groove 53b that is recessed forward from the rear end portion of the cylindrical clutch ring base portion 53a with outer irregularities. ing. The clutch ring 53 is provided in front of a ring-shaped rib 52h (see FIG. 10, FIG. 13, etc.) formed so as to project radially outward in the front opening of the outer tubular portion 52a of the gear housing 52. The groove 53b is provided so as to be rotatable around the axis.
A plurality of positioning recesses 53c are formed on the inner surface on the radially outer side of the groove 53b of the clutch ring 53 so as to be recessed radially outward at equal intervals in the circumferential direction. On the other hand, on the upper right of the front opening of the outer tubular portion 52a of the gear housing 52, a pair of protrusions 52i protruding forward is provided, and the central portion of these protrusions 52i bulges outward in the radial direction. A leaf spring 88, which is biased outward in the radial direction, is locked. The bulging portion of the leaf spring 88 can enter any of the positioning concave portions 53c, gives a click feeling to the rotation of the clutch ring 53, and positions the clutch ring 53 in the rotational direction.
A screw portion 53d having a spiral thread is provided on the inner surface of the clutch ring base portion 53a.

As shown in FIGS. 19 and 20, a ring-shaped spring holder 90 is arranged radially inward of the clutch ring 53.
On the outer surface of the cylindrical spring holder base portion 90a of the spring holder 90, a screw portion 90b having a screw thread that meshes with the screw portion 53d of the clutch ring 53 is formed. Be moved to.
The rear portion of the spring holder base portion 90a has a plurality of (12) portions projecting outward in the radial direction in a semicircular shape with respect to the front portion, and a predetermined number (4) of radially inner portions of the semicircular projecting portion. Flange portions 90c (see FIG. 15, FIG. 24, etc.) connected in total by a spring holding portion 90d (FIG. 15, FIG. 24) protruding rearward from each semicircular projection portion of each flange portion 90c in a cylindrical shape. 17, see FIG. 18, etc.). Between the flanges 90c in the circumferential direction, there are valleys 90e recessed inward in the circumferential direction with respect to the outer shape of the flanges 90c (see FIGS. 15 and 24, etc.).
A rib 90f protruding rearward from the rear end of the spring holder base 90a is provided between the predetermined spring holding portions 90d (see FIGS. 15 and 17). The rearward protruding height of each rib 90f is similar to the protruding height of the spring holding portion 90d. The ribs 90f restrict the radial outward movement of various members arranged radially inward, hold the members, and prevent them from falling off.
Further, the lower flange portion 90c has a projecting piece 90g projecting radially outward between the lower semicircular projecting portions.

As shown in FIG. 26, a clutch pin coil spring 92 as an elastic body is held in each spring holding portion 90d. Behind each clutch pin coil spring 92, a single washer 94 having the same shape as the flange portion 90c is provided. The front end of each clutch pin coil spring 92 is in contact with the rear surface of the flange portion 90c of the spring holder 90, and the rear end of each clutch pin coil spring 92 is in contact with the front surface of the washer 94.
The washer 94 has a plurality of (12 places) protrusions 94b that protrude radially outward from the ring-shaped washer base 94a in a semicircular shape. Further, between the radially outward semi-circular protrusions of the washer 94, which are adjacent to each other, there is an extended portion 94c extending radially inward from the radially inner portion of the washer base 94a. , 6 places in total. Further, a total of three troughs 94d formed in the same manner as the troughs 90e of the spring holder 90 are provided. In addition, between the protrusions 94b in the lower portion of the washer 94, a protrusion 94e protruding radially outward is provided.

As shown in FIGS. 19 to 26, the spring holder 90, the clutch pin coil spring 92, and the washer 94 are provided between the inner tubular portion 52g and the outer tubular portion 52a of the gear housing 52. The inner surface of the front portion of the outer tubular portion 52a has the same outer shape as the flange portion 90c or the washer 94. The spring holder 90 is prevented from rotating by the flange portion 94b and the protruding piece 90g. The washer 94 is prevented from rotating by the protrusion 94b and the protrusion 94e. At least one of the protrusions 90g and 94e may be omitted.
As shown in FIG. 28A, the front surface of the ring-shaped wall body portion 52j that spreads vertically and horizontally in the gear housing 52 and connects the inner tubular portion 52g and the outer tubular portion 52a has a flange portion 90c and a washer 94. It has the same shape as. A circular hole is formed in a portion of the wall portion 52j that is located on the rear side of each extended portion 94c of the washer 94, and the cylindrical hole is formed in the hole through a cylindrical clutch pin sleeve 95. Clutch pins 96 are inserted from the front.
As shown in FIGS. 28A and 28B, each clutch pin sleeve 95 projects radially outward from the cylindrical clutch pin sleeve base 95a and the outer surface of the front end of the clutch pin sleeve base 95a. And a pair of flanges 95b. The flanges 95b face each other. By providing each flange 95b, the portion supported by the gear housing 52 increases by that amount, and the front-rear length of the clutch pin sleeve 95 and the clutch pin 96 becomes shorter while maintaining the supporting strength.
Each clutch pin 96 has a cylindrical shape with a rear end rounded into a spherical shape, and the front part thereof is held integrally with the clutch pin sleeve 95 by entering the inside of the clutch pin sleeve base 95a.
The front end of each clutch pin sleeve 95 and the front end of each clutch pin 96 are in contact with the rear surface of the washer 94.
The rear end portion of each clutch pin 96 can contact the front surface of the cylindrical inner tooth portion 82a of the internal gear 82 of the front planetary gear mechanism 80.

When the clutch ring 53 is twisted and the rotational position is changed, the front and rear position of the spring holder 90 is changed, the distance between the flange portion 90c and the washer 94 is changed, and the elastic force of each clutch pin coil spring 92 is adjusted. The washer 94 pushes each clutch pin 96 via each clutch pin sleeve 95 in accordance with the elastic force of the clutch pin coil spring 92, and each clutch pin 96 causes any one of the cam projections in the internal gear 82 of the third stage. Upon hitting 82b, the internal gear 82 is rotated or restricted in accordance with the elastic force of the clutch pin coil spring 92.
That is, as also shown in FIG. 30, each clutch pin 96 presses the front surface of the internal gear 82 in accordance with the elastic force of each clutch pin coil spring 92, and when the torque is less than a predetermined torque in accordance with the elastic force, the cam projections. 82b is stopped and the internal gear 82 is fixed. The side surface of the cam projection 82b has a spherically constricted portion that conforms to the shape of the rear end portion of the clutch pin 96. By contacting the constricted portion, the clutch pin 96 can sufficiently resist the rotational force of the third-stage internal gear 82. Then, as shown in FIG. 29, when the torque becomes equal to or more than the torque, the cam projection 82b moves each clutch pin 96 forward against the elastic force to relatively get over. This overcoming is smoothly performed by the constriction unit. By this relative overcoming, each clutch pin 96 allows the rotation of the internal gear 82 so that the internal gear 82 can rotate, and if the rotation of the internal gear 82 is not blocked by another member, the internal gear 82 is prevented from rotating. The rotation of the null gear 82 causes the carrier 86 (each projection 86c) to idle, and the clutch operates.
The spring holder 90, the clutch pin coil springs 92, the washers 94, the clutch pin sleeves 95, and the clutch pins 96 are components of the clutch mechanism 99. The clutch mechanism 99 may include the cam protrusion 82b. Further, at least one of the clutch pin sleeve 95 and the washer 94 may be omitted.
In the electric vibration driver drill 1, the coil spring 92 for each clutch pin is not divided into one large one but is divided into a plurality (12 pieces), so that the spring constant is increased more than in the case of one large coil spring. Also, the contact length can be made smaller, and the length in the front-rear direction becomes shorter. Further, various members can be arranged between the clutch pin coil springs 92 without interfering with the operation of the coil springs 92 for clutch pins, and the electric vibration driver drill 1 becomes compact accordingly.

As shown in FIG. 24 and FIG. 25, a support ring 100 and a pin holder 102 on the rear side are arranged inside the spring holder 90 in the radial direction.
The support ring 100 has a plurality of trapezoidal cam protrusions 100b (three locations) formed so as to project forward from other portions at the front end of a cylindrical support ring base 100a whose axial direction is the front-back direction. , Are in a state of being equidistant from each other in the circumferential direction (see FIGS. 15 and 20). Further, a plurality of (three places) protrusions 100c protruding rearward from the rear end of the support ring base 100a are arranged between the cam protrusions 100b in the circumferential direction (see FIG. 15 and the like).
The pin holder 102 includes a recess 102b (see FIG. 15 and the like) provided at the front end of a cylindrical pin holder base portion 102a whose axial direction is the front-rear direction so as to correspond to the projecting piece 100c of the support ring 100, and a pin holder base portion, respectively. A plurality (six places) of spring holding portions 102c (see FIG. 15, etc.) that project radially inward and rearward from the inner surface of 102a and are arranged at equal intervals in the circumferential direction, and a radial direction from the outer surface of the pin holder base portion 102a, respectively. And a plurality of (three places) pin holding portions 102d that project outward and are arranged at equal intervals in the circumferential direction. The recess 102b and the pin holding portion 102d are displaced from each other in the circumferential direction.
The front end of the pin holder coil spring 104 as an elastic body is inserted in the rearward projecting portion of each spring holding portion 102c. The rear part of the pin holder coil spring 104 is provided in recesses 52k (see FIG. 25, FIG. 28 (a), etc.) formed so as to be recessed in a cylindrical shape from the front surface of the wall body portion 52j of the gear housing 52 to the rear. The depressions 52k are formed at a total of 6 positions in the same arrangement as the spring holding portion 102c. The pin holder coil spring 104 biases the pin holder 102 forward.
As shown in FIGS. 24 and 25, each pin holding portion 102d holds the front end portion of a cylindrical internal gear lock pin 106 extending in the front-rear direction. A ring-shaped groove is formed in the front end portion of the internal gear lock pin 106, and the tip portion of the bifurcated pin holding portion 102d is inserted in the groove. The pin holding portions 102d and the internal gear lock pins 106 pass between predetermined clutch pin coil springs 92 and outside the spring holder 90 and the valleys 90e and 94d of the washer 94 (see FIGS. 24 and 26, etc.). ). Further, each pin holding portion 102d passes through a corresponding pin hole 52l formed in the wall portion 52j of the gear housing 52 (see FIG. 25). The rear end portion of each pin holding portion 102d can advance and retreat toward the radially outer side of the third-stage internal gear 82.

As shown in FIG. 21, the mode switching ring 54 has a cylindrical cylindrical shape with a tapered frontward concavo-convex, and a mode switching ring base 54a that protrudes rearward from the rear end of the inner surface thereof. And a cam portion 54b.
The cam part 54b has a total of three trapezoidal cam recesses 54c, which are arranged in the same manner as the cam protrusions 100b of the support ring 100 (see FIGS. 15, 19, 36, 39, etc.). The support ring 100 is arranged on the rear side of the cam portion 54b.
Further, as shown in FIGS. 11, 13, 15, and 40, the rotation restriction that protrudes radially inward on the inner surface of the mode switching ring 54 and on the front side of the cam portion 54b. Ribs 54d are provided. A rotation permitting recess 54e that is recessed radially outward is formed on the upper portion of the rotation restricting rib 54d. A pair of plate spring locking portions 54f for locking the plate spring 114 as an elastic body is formed below the rotation restricting rib 54d.

The mode switching ring 54 is rotatably attached around an axis in a state where the cam portion 54b is arranged radially outward of the inner tubular portion 52g of the gear housing 52. A ring-shaped retainer 110 is fixed to the front end portion of the inner tubular portion 52g by a plurality (four) screws 112. The mode switching ring 54 is sandwiched between the retainer 110 and the clutch ring 53.
As shown in FIGS. 11 and 40, the retainer 110 includes a ring-shaped retainer base portion 110a, screw holes 110b formed in the retainer base portion 110a through which the screws 112 pass, and a radial direction from the outer side of the retainer base portion 110a. The protrusion 110c protruding outward and a plurality of (three) notches 110d recessed radially inward from the outer side of the retainer base 110a on the side facing the protrusion 110c.
The screw holes 110b are arranged so as not to be rotationally symmetrical with respect to the center of the retainer base 110a. A plurality of screw hole portions 52m, which are arranged similarly to the screw holes 110b and receive the screws 112, are formed at the front end portion of the inner cylinder portion 52g. The non-rotationally symmetrical arrangement of the screw holes 110b and the screw hole portions 52m prevents the retainer 110 from being attached in the wrong orientation.
The projecting piece 110c is located in the rotation allowing recess 54e of the mode switching ring 54 when viewed in the circumferential direction.
The notches 110d are arranged at equal intervals in the circumferential direction within a predetermined arc. A radially inwardly bulged portion of the leaf spring 114 can enter any one notch 110d.
The mode switching ring 54 is rotated from the state where the leaf spring 114 enters the central notch 110d (center state, see FIG. 11) to the left when viewed from the rear against the biasing force of the leaf spring 114. 114 enters the right notch 110d (left state, see FIG. 40). At this time, the projecting piece 110c is located at the end of the rotation permitting recess 54e, and further rotation to the left is restricted by the rotation restricting rib 54d. Similarly, when the plate spring 114 is turned to the right from the center state, the leaf spring 114 enters the left notch 110d (the right state), and further rotation to the right is restricted.

As shown in FIGS. 25 and 27, a plurality of (five) steel balls 120 as sliding members are provided between the mode switching ring 54 and the clutch ring 53.
Five recesses 54g, which are recessed forward from the rear surface of the mode switching ring base 54a, are arranged at equal intervals in the circumferential direction. A ball 120 is inserted into each recess 54g via a steel disc 122. On the other hand, a ring-shaped groove 53e is formed on the front surface of the clutch ring base 53a, and a steel washer 124 is inserted in the groove 53e. The rear portion of each ball 120 is in contact with the washer 124.
When the mode switching ring 54 and the clutch ring 53 rotate relatively, each ball 120 rolls between the disk 122 and the washer 124, and the friction between the mode switching ring 54 and the clutch ring 53 is reduced.

As shown in FIG. 11, FIG. 30, and FIG. 36 to FIG. 39, when the mode switching ring 54 is in the central state or the right state, the portions of the cam portion 54b other than the cam concave portion 54c are the respective cam protrusions of the support ring 100. The support ring 100 contacts the front end of 100b and is located rearward. Then, the pin holder 102 is located rearward, and the internal gear lock pins 106 are located radially outside the third-stage internal gear 82 and between the protruding portions 82c in the circumferential direction. Each of the internal gear lock pins 106 blocks rotation of the third-stage internal gear 82 by hitting a side surface of the protrusion 82c.
On the other hand, as shown in FIGS. 40 to 42, when the mode switching ring 54 is in the left state, the cam projections 100b enter the cam recesses 54c, and the support ring 100 is located in the front. Then, the pin holder 102 is located in the front, and each internal gear lock pin 106 is retracted from the radially outer side of the third-stage internal gear 82. Therefore, each internal gear lock pin 106 does not hinder the rotation of the third-stage internal gear 82. Therefore, the third-stage internal gear 82 starts to rotate with a torque according to the rotational position of the clutch ring 53, and the clutch operates (clutch mode).
The support spring 100 is urged by the pin holder coil springs 104 via the pin holders 102, so that the cam protrusions 100b enter the cam recesses 54c. When the mode switching ring 54 is rotated from the left state to another state, each cam projection 100b separates from the cam recess 54c against the biasing force of each pin holder coil spring 104, and the pin holder 102 is located rearward.

As shown in FIG. 28A, the rollers 130 are respectively arranged in a pair (left and right in the figure) facing each other between the protrusions 86c of the third stage carrier 86.
A lock cam 132 is arranged in the other pair (upper and lower in the figure). The lock cam 132 has a cylindrical portion 132a and a pair of projecting pieces 132b projecting radially outward from the top and bottom of the cylindrical section 132a, and each projecting piece 132b is located between the projecting bodies 86c. There is. The central hole in the cylindrical portion 132a of the lock cam 132 and the rear stage portion 55d of the spindle 55 are spline-connected, and the lock cam 132 is integrated with the spindle 55. The lock cam 132 rotates together with the carrier 86 of the third stage via each of the protrusions 86c.
A cylindrical lock ring 134 is covered on the front side of the lock cam 132. The lock ring 134 is fixed inside the inner tubular portion 52g of the gear housing 52. The lock ring 134 includes a cylindrical lock ring base portion 134a, an inner flange 134b projecting inward from a front end inner surface thereof, an outer flange 134c projecting outward from a rear end outer surface of the lock ring base portion 134a, and a lock. A plurality of (three places) protruding portions 134d that are arranged at equal intervals in the circumferential direction and that protrude outward in the radial direction from the side surface of the ring base portion 134a and further protrude forward. The rollers 130, the lock cams 132, and the protrusions 86c of the third-stage carrier 86 are located behind the inner flange 134b. The locking portion 134d is fixed in a non-rotatable manner by the protruding portion 134d entering the inner surface of the inner cylindrical portion 52g of the gear housing 52 formed in a corresponding shape.

As shown in FIGS. 15 to 18 and 26, the spindle 55 includes a spindle rear bearing 138 arranged on the front side of the lock ring 134 and a spindle front bearing 140 arranged radially outside the front stage portion 55b. It is held so as to be movable back and forth and rotatable about an axis.
The spindle front bearing 140 is arranged outside the front stage portion 55b of the spindle 55.
A coil spring 144 for the spindle, which is an elastic body, is provided between the spindle front bearing 140 and the spindle flange 55a. The rear surface of the spindle flange 55a and the coil spring 144 for the spindle have a taper shape of which the diameter gradually expands toward the front and spreads forward.
On the other hand, a clip 146 for pressing the spindle rear bearing 138 (the front surface of the outer ring thereof) is inserted in a groove provided on the inner surface of the inner cylindrical portion 52g of the gear housing 52.

As shown in FIGS. 14, 16 to 18, FIG. 19, FIG. 20, and FIG. 22, a vibration mechanism 150 is arranged between the spindle front bearing 140 and the clip 146. The vibration mechanism 150 has a first vibration cam 152 and a second vibration cam 154, each of which is ring-shaped and is held by the middle stage portion 55c of the spindle 55.
A first cam surface 152b having a plurality of cam teeth is formed on the rear surface of the cylindrical first vibration cam base portion 152a of the first vibration cam 152. The first vibration cam 152 is integrally fixed to the spindle 55 by a circlip 156 fixed to the outside of the front end portion of the middle stage portion 55c of the spindle 55. The spindle 55 is normally urged by the spindle coil spring 144 to a forward position where the circlip 156 contacts (the inner ring of) the spindle front bearing 140.
A second cam surface 154b having a plurality of cam teeth is formed on the front surface of the ring-shaped second vibration cam base portion 154a of the second vibration cam 154. In addition, a plurality of (three) claws 154c protruding rearward are provided on the rear surface of the second vibration cam base 154a at equal intervals in the circumferential direction. The second vibration cam 154 is inserted into the spindle 55 in a state where it is not fixed in the circumferential direction.
A ball holding washer 160, a plurality of steel balls 162, and a ball receiving washer 164 are provided between the second vibration cam 154 and the clip 146.
As shown in FIG. 22, the ball holding washer 160 is adjacent to the rear surface of the second vibration cam base 154a. The ball holding washer 160 has a bowl shape having an inner peripheral portion as a front end and an outer peripheral portion as a rear end, holds the balls 162 on the curved rear surface side, and arranges the balls 162 in the circumferential direction.
As shown in FIG. 23, the ball receiving washer 164 has a plurality (three places) of convex portions 164b that are radially outwardly projected from the ring-shaped ball receiving washer base portion 164a and are arranged at equal intervals in the circumferential direction. And a constricted portion 164c respectively arranged between the convex portions 164b in the circumferential direction. The ball receiving washer 164 is prevented from rotating by the protrusions 164b entering the recesses 52n provided on the inner surface of the inner cylindrical portion 52g of the gear housing 52.
At least one of the circlip 156, the ball holding washer 160, the ball 162, and the ball receiving washer 164 may be included in the vibration mechanism 150.

As shown in FIGS. 15 to 24, a vibration switching ring 170 is provided inside the cam portion 54b of the mode switching ring 54 in the radial direction. On the rear side of the vibration switching ring 170, a set (3) of vibration switching levers 172 (a vibration switching member, a part of the vibration switching means) which is an arc shape of a third of the entire circumference is provided. There is. A washer 174 is provided on the rear side of the vibration switching lever 172.
The vibration switching ring 170 includes a plurality (three places) of protrusions 170b, which are radially outwardly projected from the front end of a cylindrical vibration switching ring base 170a and are arranged at equal intervals in the circumferential direction, and a vibration switching ring base. A plurality of trapezoidal cam recesses 170c are provided at the same position as the protrusions 170b in the circumferential direction (three places), which are recessed forward from the rear end of the 170a. Each of the protrusions 170b fits into a corresponding recess 54h (see FIG. 13) provided at the rear of the cam portion 54b of the mode switching ring 54, and the vibration switching ring 170 is integrated with the mode switching ring 54. Rotate.
Each of the vibration switching levers 172 has a vibration switching lever base 172a having a U-shaped cross section that is opened forward, and a ridge 172b that bulges forward in a shape corresponding to the cam recess 170c in the vibration switching lever base 172a (FIG. 17). , Etc.), and a vibration switching claw 172c (see FIGS. 22, 23, etc.) projecting radially inward and rearward from the center of the radially inner outer surface of the vibration switching lever base 172a. Each of the vibration switching levers 172 has a plurality of (three) radial holes 52o (through holes, see FIG. 15) formed at equal intervals in the circumferential direction in the central portion of the inner cylindrical portion 52g of the gear housing 52 in the front-rear direction. The vibration switching claw 172c is inserted in the inner cylindrical portion 52g in the radial direction outside. The vibration switching lever 172 is arranged inside the support ring 100.
As shown in FIGS. 22 and 23, each vibration switching claw 172c is located radially outside the constricted portion 164c of the ball receiving washer 164. That is, the ball receiving washer 164 has a constricted portion 164c that avoids each vibration switching claw 172c.
Further, each of the vibration switching claws 172c can move back and forth between the claws 154c protruding rearward on the rear side of the second vibration cam base 154a.

Pin holes 52p extending in the front-rear direction are formed in portions of the inner tubular portion 52g of the gear housing 52 that are adjacent to the six recesses 52k in the circumferential direction between the three holes 52o (FIG. 21, see FIG. 27, etc.). A pin 180 is inserted from the rear into each pin hole 52p. The front portion of each pin hole 52p is enlarged with respect to the rear portion, and a vibration switching lever coil spring 182, which is an elastic body, is inserted between the enlarged portion and the front portion of each pin 180. The front end portion of each vibration switching lever coil spring 182 is in contact with the rear washer 174 of each vibration switching lever 172. Each vibration switching lever coil spring 182 biases the washer 174 and each vibration switching lever 172 forward.
That is, the vibration switching lever coil springs 182 as biasing members are arranged in the circumferential direction in three or more (six), and a plurality of vibration switching levers 172 are in contact with each other (two). The vibration switching lever coil spring 182 biases (presses) the vibration switching lever 172.
As shown in FIG. 22 and FIG. 23, when the mode switching ring 54 is in the central state or the left state, the portions other than the cam recessed portion 170c at the rear end of the vibration switching ring base 170a are the protrusions of each vibration switching lever 172. The vibration switching levers 172 are located rearward, contacting the front end of the portion 172b. Then, each vibration switching claw 172c is located rearward and separated from the space between the claws 154c of the second vibration cam 154, and each vibration switching claw 172c performs the rotation so that the second vibration cam 154 can rotate. Tolerate. When the spindle 55 rotates, the first vibration cam 152 rotates integrally, and the second vibration cam 154 also rotates appropriately via the first cam surface 152b and the second cam surface 154b, where the second vibration cam 154 is the spindle. Since it is inserted in 55 and rotation is allowed, no vibration occurs.
On the other hand, as shown in FIG. 38, when the mode switching ring 54 is in the right state, the corresponding raised portions 172b are inserted into the respective cam concave portions 170c, and the respective vibration switching levers 172 are located forward. Then, each vibration switching claw 172c is located in the front and enters between the claws 154c of the second vibration cam 154, and even if the second vibration cam 154 tries to rotate, each vibration switching claw 172c is caught on the claw 154c. Then, each vibration switching lever 172 blocks rotation of the second vibration cam 154 by each vibration switching claw 172. When the spindle 55 rotates, the first vibration cam 152 rotates integrally, whereas the second vibration cam 154 does not rotate. Therefore, when the spindle 55 retracts, the first cam surface 152b fixes the fixed second cam surface 152b. The surface rotates in contact with the surface 154b, and vibration in the axial direction occurs on the spindle 55 (vibration mode). In the electric vibration driver drill 1, the vibration switching ring 170, the vibration switching levers 172, the pins 180, and the coil springs 182 for the vibration switching levers constitute vibration switching means.
When each vibration switching lever 172 is located in front, the rear end of the vibration switching ring base 170a relatively enters into each vibration switching lever base 172a, and the closeness of contact of each vibration switching lever 172 and the vibration switching ring 170 The degree of contact with each vibration switching lever 172 increases. Therefore, when a vibration occurs, the blockage property is secured in the part in front of each of the vibration switching levers 172 (inside the inner cylindrical part 52g of the gear housing 52), the dustproof property is secured, and it is applied in the part. Grease leakage is prevented.
Further, the vibration switching lever coil springs 182 urge the vibration switching levers 172 forward to promote the entry of the raised portions 172b into the cam recesses 170c. When the mode switching ring 54 is rotated from the right state to another state, the raised portions 172b are separated from the cam recesses 170c against the urging force of the vibration switching lever coil springs 182, and the vibration switching levers 172 move. Located behind.

An operation example of such an electric vibration driver drill 1 will be described.
When the operator grips the grip portion 6 and pulls the switch lever 8, power is supplied from the battery 32 to the motor 10 by switching in the switch body portion 9, and the rotor 41 (motor shaft) rotates.
The fan 44 rotates due to the rotation of the motor shaft. Exhaust to the exhaust ports 22a of the fan 44 causes a flow (air) of air from the intake port 20c. Such a wind cools the mechanism inside the housing 2 including the motor 10.

Further, the rotational force of the motor shaft is reduced by the gear assembly 12 having a three-stage reduction mechanism and transmitted to the spindle 55 and transmitted to a bit such as a drill or a driver attached to the chuck 14.
The middle planetary gear mechanism 70 of the gear assembly 12 operates in the high speed mode or the low speed mode depending on the position of the speed switching lever 79.

Furthermore, three operation modes can be selected according to the rotational position of the mode switching ring 54.
That is, when the mode switching ring 54 is in the left state, the clutch mode is selected, and when the torque corresponding to the rotational position of the clutch ring 53 is applied to the spindle 55, the front planetary gear mechanism 80 idles to disengage the clutch. (Torque transmission is stopped). When the screw tightening is advanced by the driver bit and the screw enters completely and a large torque is applied, the spindle 55 idles to complete the screw tightening.
On the other hand, when the mode switching ring 54 is in the right state, the vibration mode is selected, each vibration switching lever 172 locks the rotation of the second vibration cam 154, and the spindle 55 moves backward during rotation, so that the first cam surface 152b. And the second cam surface 154b rub against each other, and an axial vibration is generated in the spindle 55.
On the other hand, when the mode switching ring 54 is in the central state, the internal gear 82 of the front planetary gear mechanism 80 is fixed and the rotation of the second seismic cam 154 is allowed, so that the clutch does not operate and seismic vibration occurs. The drill mode will not occur. In the drill mode, the spindle 55 is rotated without disengaging the clutch, and when the worker mounts the drill bit and advances the drilling, the rotation of the spindle 55 is continued regardless of the load on the spindle 55.

The above-described electric vibration driver drill 1 includes a housing 2 (gear housing 52), a mode switching ring 54 (first ring) and a clutch ring 53 (second ring) rotatably mounted on the housing 2, respectively. Each ball 120 (sliding member) arranged between the mode switching ring 54 and the clutch ring 53. Therefore, friction between the mode switching ring 54 and the clutch ring 53 is reduced, and the mode switching ring 54 and the clutch ring 53 are easily rotated.
Further, since the sliding member is each ball 120, the sliding member can be arranged more easily than when it is a cylindrical bearing.
Further, each disc 122 is interposed between the mode switching ring 54 and each ball 120, and a washer 124 is interposed between the clutch ring 53 and each ball 120. Therefore, compared with the case where each ball 120 directly contacts the mode switching ring 54 or each ball 120, the rotation of each ball 120 becomes smoother, and the life of each ball 120, the mode switching ring 54, and the clutch ring 53 becomes longer. become longer.

Further, the electric vibration driver drill 1 can operate the housing 2 (gear housing 52), the vibration mechanism 150 and the clutch mechanism 99 arranged inside the housing 2, and the vibration mechanism 150, and can rotate in the housing 2. The mode switching ring 54 (vibration switching ring) held by the clutch mechanism 99 and the clutch ring 53 (clutch switching ring) rotatably held in the housing 2, the mode switching ring 54 and the clutch ring. 53 and each ball 120 disposed between the two. Therefore, friction between the mode switching ring 54 and the clutch ring 53 is reduced, and the mode switching ring 54 and the clutch ring 53 are easily rotated.
Further, the mode switching ring 54 operates whether or not the vibration of the spindle 55 (output shaft) by the vibration mechanism 150 is in the vibration mode (right state), and the clutch ring 53 is the clutch of the clutch mechanism 99. Is operated by changing the rotational position. Therefore, the mode switching ring 54 and the clutch ring 53, which are easily rotated, make it easy to command the presence or absence of vibration and the clutch operating torque.

In addition, the electric vibration driver drill 1 includes a motor 10, a spindle 55 rotatable by the motor 10, a first vibration cam 152 fixed to the spindle 55, and a housing in which the first vibration cam 152 is arranged inward. 2 (gear housing 52), a second vibrating cam 154 arranged inside the housing 2 and capable of rubbing against the first vibrating cam 152, and whether or not the second vibrating cam 154 can rotate with respect to the housing 2. It has each vibration switching lever 172 to be switched, and a plurality of (two in total, six in total) vibration switching lever coil springs 182 for biasing each vibration switching lever 172. Therefore, each of the vibration switching lever coil springs 182 applies a plurality of vibration switching lever coil springs 182 with a biasing force (elastic force) for pushing each vibration switching lever 172 forward and switching to the vibration mode. And the size of each piece can be reduced. Therefore, the electric vibration driver drill 1 having a compact vibration switching means and thus the whole is provided.
Further, three or more coil springs 182 for the vibration switching lever are provided and arranged in the circumferential direction. Therefore, while ensuring the switching to the vibration mode, the vibration switching means, and thus the whole, becomes compact especially in the front-rear direction.
Further, a plurality (three) of the vibration switching levers 172 are provided and arranged in the circumferential direction. Therefore, the vibration switching lever 172 can be easily assembled around the vibration mechanism 150, and the rotation of the second vibration cam 154 can be more reliably prevented.
In addition, the second vibration cam 154 has a pawl 154c, the vibration switching lever 172 has a vibration switching pawl 172c, and the vibration switching pawl 172c is applied to the pawl 154c, so that the second vibration cam Block rotation of 154. Therefore, the vibration switching lever 172 can reliably switch the rotation of the second vibration cam 154 with a simple configuration.

It should be noted that the modes and modified examples of the present invention are not limited to the above modes and modified examples, and for example, the following further modifications can be appropriately made.
At least one of the disc 122 and the washer 124 may be omitted. The disc 122 may be arranged on the clutch ring 53 side, or the washer 124 may be arranged on the mode switching ring 54 side. The disc 122 may be arranged on both sides, or the washer 124 may be arranged on both sides.
Further, instead of the ball 120 or together with the ball 120, a resin washer (sliding member) having a smooth front surface and a rear surface may be used. When the ball 120 is not used, the mode switching ring 54 and the clutch ring 53 slide on the smooth surface of the washer, and the friction is reduced.
These arrangements may be changed such that the mode switching ring 54 is on the rear side of the clutch ring 53. Further, at least one of the mode switching ring 54 and the clutch ring 53 may be changed to another ring which is externally mounted on the housing 2 or which can be operated by an operator.
The clutch mechanism 99 may be an electronic clutch. The vibration mechanism 150 may electrically generate vibrations. The vibration mechanism 150 may be omitted, and the electric driver drill may have no vibration mode. The clutch mechanism 99 may be omitted, and a vibration drill having no clutch mode may be used. The drill mode may be omitted and the vibration driver may be provided without the drill mode.

The holding of the internal gear lock pin 106 by the pin holding portion 102d may be performed in other forms such as press fitting the protrusion into the hole. Other forms such as holding or press fitting may be similarly changed as appropriate.
The fan 44 may be arranged in front of the stator 40.
The battery 32 may be any lithium-ion battery of 18 to 36V, such as 14.4V, 18V (maximum 20V), 18V, 25.2V, 28V, 36V, and the like, which has a voltage of less than 10.8V or more than 36V. Lithium-ion batteries can be used, or other types of batteries can be used.
The gear housing 52 may be retained in the main body housing 20.
Number of sections of the housing 2, number of planetary gears installed, number of stages of reduction mechanism, number of various balls, number of rollers 130, number of various protrusions (projections, protrusions, protrusions, etc.), various pins And / or the number of various springs and / or the number of various screws may be increased or decreased with respect to the above number. The materials of various members may be changed such that the steel balls are made of resin. The type of various operating parts such as the type of switch of the switch lever 8 may be changed. The arrangement of various members or parts may be changed such that the spring holder 90 of the clutch mechanism 99 is arranged radially inside the pin holder 102 for locking the internal gear 82. The shape of various members may be changed such that the circular plate 122 is a regular polygonal plate.
Further, the direction of the output shaft (tip tool holding part) is different from the direction of the power part (at least one of the direction of the motor shaft of the motor and the transmission direction of the mechanism for transmitting its rotational force) (approximately 90 degrees). The present invention may be applied to an angle power tool.
Further, a non-rechargeable (battery-powered) vibration driver drill including those driven by a commercial power source, or an electric tool other than the vibration driver drill, or a gardening tool such as a cleaner, a blower, or a trimmer for gardening. The present invention may be applied to the above.

  1 ... Electric vibration driver drill (electric power tool), 2 ... Housing, 10 ... Motor, 52 ... Gear housing, 55 ... Spindle, 150 ... Vibration mechanism, 152 ... First vibration cam, 154 ... Second vibration cam, 154c ··· claw, 172 · · vibration switching lever (vibration switching member), 172c · · vibration switching pawl, 182 · · coil spring for the vibration switching lever (biasing member).

Claims (4)

A motor,
A spindle rotatable by the motor,
A first seismic cam fixed to the spindle;
A housing in which the first vibration cam is arranged inward,
A second seismic cam that is disposed inside the housing and is capable of rubbing against the first seismic cam;
A vibration switching member that switches whether the second vibration cam can rotate with respect to the housing;
A plurality of biasing members for biasing the vibration switching member,
An electric tool characterized by having. The power tool according to claim 1, wherein three or more urging members are provided and arranged in the circumferential direction. The power tool according to claim 1, wherein a plurality of the vibration switching members are provided and arranged in the circumferential direction. The second vibration cam has a claw,
4. The vibration switching member has a vibration switching claw, and the vibration switching claw is applied to the claw to prevent rotation of the second vibration cam. The electric tool according to any of the above.

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