JPS62224584A - Power tool - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

Detailed Description of the Invention [Technical Field 1] The present invention relates to a power tool equipped with an iut*N/I transmission.6 [Background Art] In the transmission Vcv1, the rotation of an internal gear in a component of a planetary mechanism When shifting gears by controlling the IU gear, a system in which the internal gear is fixed or connected to a carrier supporting the IU gear and rotates together with the carrier is used to shift gears. 51-47185. However, with this one, when the internal gear is fixed, it becomes normal planetary 8! However, when the internal gear is connected to the carrier, the sun gear and the carrier are directly connected, so there is no deceleration, and even though the speed can be changed, there is a relatively large deceleration caused by power tools. For those that require a high ratio, shifting is not actually effective.

[U-Objective of the Invention] The present invention has been made in view of the above points, and its purpose is to provide a power tool equipped with a transmission device capable of selecting a plurality of transmission ratios. .

[Disclosure of the Invention] Accordingly, the present invention is provided with a transmission in which the 'iIL Star Isokare' is installed in two stages, which is composed of a sun gear, an internal gear, a planetary gear that meshes with both of these gears, and a carrier that supports the M star gear. The internal gear in one of the planetary gears is made to be able to slide freely in the ring direction and freely rotate around the pongee, and the engagement protrusions provided on the inner surface of the gear case housing these planetary mechanisms and the carrier or sun gear are provided. The feature is that the internal gear can be freely engaged with the engagement protrusion by moving in the ring direction, and even when the input/output of one planetary mechanism is directly connected, the 'i! This is to ensure that the speed change due to L Hoshiiso's disease is effective.

Hereinafter, the present invention will be described in detail based on the illustrated embodiment. The illustrated example is incorporated into a speed reducer 3 in a power system assembly of an electric drill driver, and this assembly is a first
As shown in Figure 0, the clutch handle 78 and chuck 8 are used for tightening the clutch 2, gear case 6, and torque adjustment.
It is composed of. Disposed within the gear case 6 are a speed reduction section 3 having a variable coupling function and a torque adjustment clutch section 4 having a locking means.

The deceleration section 3 and clutch section 4 will be explained based on FIGS. 1 and 2. First, the gear case 6 includes a cylindrical case 61 and a mounting screw 6 attached to the front end of the case 61.
4, and a motor mounting base 60 attached to the rear end of the case 61. In addition, the case 61 has a pair of elongated holes 6 extending in the ring direction.
3 and a pair of support pins 65 protruding from the outer surface, the case 62 is provided with a plurality of holes 67 penetrating in the ring direction, and the case 62 has an irregular trapezoid whose cross-sectional shape is non-circular from the front end. A portion 66 is integrally provided in a protruding manner.

The reduction gear g3 installed in the case 61 of the gear case 6 is composed of two stages of M Hoshi Isojo,
The first stage planetary mechanism includes a sun gear 31 fixed to the output shaft 20 of the motor 2, an internal gear 33 fixed to the inner surface of the case 61, and a plurality of planetary gears 3 that mesh with both.
2, and a carrier 34 equipped with a shaft that supports each planetary gear 32, and the second stage planetary gear structure is the carrier 34.
Sun gear 35 and internal gear 3 integrally formed with
7, a plurality of planetary gears 36, and a carrier 38 that supports each planetary gear 36.

Here, although the internal gear 33 is fixed to one case 611 as described above, it is large in size, and the internal gear 37 is slidable in the ring direction and rotatable around the ring, and the outer periphery of the internal gear 33 is large. There is an annular groove 5 in the center of the surface.
2 are formed, and a plurality of engagement teeth 51 are provided at equal intervals in the circumferential direction on one end side of the outer peripheral surface. Further, the outer peripheral surface of the internal gear 37 is received by a plurality of roller pins 71 arranged at intervals on the inner peripheral surface of the case 61, as shown in FIG.

The internal gear 37 is moved in the ring direction by a lever 55 whose ends are engaged with an annular groove 52 on the outer circumferential surface of the internal gear 37 via rollers 56 and 56, respectively. As shown in FIGS. 4 and 10, the lever 55, which has a two-character shape and has a handle 58 connected to its central portion, is separated from both sides by a pair of support pins 65 protruding from the outer surface of the case 61. It is rotatably supported, and rollers 56, 56 are attached to the U-shaped folded ends of both sides, respectively, and are engaged with the internal gear 37 through elongated holes 63° 63 formed in the case 61. It is something that
Since it is made of wire, it has spring properties.

On the other hand, in the planetary mechanism of the first stage 1, an engaging protrusion 54 is provided on the outer circumferential surface of the carrier 34, and a plurality of engaging protrusions 53 are provided on the inner circumferential surface of the case 61.

These engaging protrusions 54 and 53 engage with the teeth on the inner peripheral surface of the internal gear 37 and the engaging teeth 51, respectively, when the internal gear 37 slides in the ring direction, and are provided at the center of the lever 55. When the internal gear 37 is advanced by retracting the internal gear 37 and the engaging tooth 51 is engaged with the engaging protrusion 53 provided on the case 61, as shown in FIGS. 37 is prevented from rotating. Conversely, by moving the central part of the lever 55 forward, the internal gear 37 is moved backward, and as shown in FIG.
In order to engage the internal gear 37, the internal gear 37 and the sun gear 35 integrally provided on the carrier 34 are coupled. In any case, the engagement between the internal gear 37 and the planetary gear 36 is maintained.

In the former case, the second-stage planetary mechanism also effectively decelerates, resulting in a large reduction ratio, and in the latter case, the planetary gear 36 controls the rotation (rotation) around the pongee. Since the sun gear 35 and the carrier 38 are directly connected, only the speed reduction of the first stage planetary mechanism is effective, and therefore the speed reduction ratio becomes small. By the way, the number of teeth of both sun gears 31.35 is z3. , Z, 5, the number of teeth of both internal gears 33.37 is Z 331 Z 3
7, the reduction ratio P of the entire reduction unit 3 in the former case and the reduction ratio P2 in the latter case are as follows.

Further, when the internal gear 37 is connected to the carrier 34, it constantly rotates, but as mentioned above, the outer circumferential surface is received by the roller bin 71, and the engagement part between the internal gear 37 and the lever 55 is Since the roller 56 is also provided, the increase in frictional load is small and the noise is low.

Further, the movement of the lever 55 for moving the internal gear 37 can be transmitted to the internal gear 37 through the springiness of the lever 55 itself.

In other words, the internal gear 37 moves by being pushed by elasticity, and by reducing the number of engagement teeth 51 and engagement protrusions 53 of the internal gear 37, the engagement between the internal gear 37 and the engagement protrusions 53 is reduced. It is possible to make it smooth and reliable.

Next, the clutch section 4 for torque adjustment will be explained.

This clutch section 4 is similar to the speed reduction section 3 described above. It utilizes Hoshiisokare and has a torque of 1llW″F.
, In addition to the stages, a locking means for preventing rotation of the output shaft 7 in both directions is also incorporated, and the 'i!' is disposed inside the case 62. The L star mechanism includes a sun gear 40, an internal gear 42, and an internal gear 42, which are integrally formed with the carrier 38.
A plurality of planetary gears 41 that mesh with these two gears and a carrier 43 that supports each planetary gear 41 form a hη configuration.

The locking means includes a plurality of cam protrusions 47 protruding from the inner periphery of the front end of the internal gear 42 at equal intervals in the circumferential direction, and a pair of locking pins 45a rotatably attached to the inner surface of the case 62. , 45b, the central part is supported by the case 62, and both ends are connected to each lock bin 4.
5a and 45b, and a lock ring 44 which is coupled to the output shaft 7 together with the carrier 43 so as to rotate integrally therewith.

Each of the lock bins 45a and 45b engages with the teeth on the outer circumference of the lock ring 44 so as to form a ratchet with their ends facing each other. Six lock bins 45a and 45b prevent rotation in one direction, and the lock bin 45b prevents rotation in the other direction of the output shaft 7.
4, the output shaft 7, to which the chuck 8 is fixed by the mounting screw 80, is locked against rotation in both directions.

Torque i again! ! The means includes a plurality of locking protrusions 48 protruding from the outer periphery of the front end of the internal gear 42 at equal intervals in the circumferential direction, and disposed within the plurality of holes 67 formed in the case 62. A ball 74, a thrust plate 75 that covers the irregularly shaped table part 66 of the case 62, a clutch spring 76,
It is composed of a clutch plate 77 and the clutch handle 78.

The clutch handle 78 has a mounting plate 79 attached to the end surface of the gear case 6 and the gear case 6 with mounting screws 81.
It is designed to be able to rotate freely within a predetermined angle by opening the clutch handle 78, and its inner surface has an engaging part with the clutch plate 77, so that when the clutch handle 78 is rotated, the irregularly shaped base of the case 62 can be rotated freely. A clutch plate 77, which is prevented from rotating by fitting with the portion 66, is configured to move in the wheel direction. The clutch spring 76 is a compression coil spring disposed between the clutch plate 77 and the thrust plate 75, and comes into contact with the steel ball 74 via the thrust plate 75. steel ball 7
4 engages with the locking protrusion 48 formed on the internal gear 42.

The operations of the locking means and torque adjusting means in the clutch section 4 will be explained. In a stopped state where the motor 2 is not rotating, a pair of lock bins 45a and 45b
are both engaged with rock song 44, and output as described above! lll7 is locked for rotation in both directions. Therefore, the tightening operation can be performed manually.

Now, if you try to rotate the motor 2 from this state and rotate the output shaft 7 in one direction, since the output shaft 7 is locked, this driving force will be transferred to the internal gear 42 via the planetary gear 41. As a result, the internal gear 42 rotates in the opposite direction, and when the locking protrusion 48 comes into contact with the ball 74 biased by the clutch spring 76 and its rotation is stopped, the internal gear 42 rotates in the opposite direction. The cam protrusion 47 pushes one of the pair of lock bins 45a, 45b according to the direction of rotation to separate it from the lock song 44, thereby releasing the restriction on rotation of the output shaft 7 in one direction. Since the other lock bin does not prevent the output shaft 7 from rotating in this direction,
The output shaft 7 starts rotating due to the power from the motor 26. From then on, this state is maintained in the locking means, but the tightening is performed by receiving the reaction force when the torque reaches a predetermined value. Internal gear 42 starts rotating. In other words, the spring-biased steel ball 74 is held by the locking protrusion 48.
gets over it and starts rotating. As a result, the torque transmitted to the output shaft 7 is limited at that point, and the output shaft 7
is stopped.

In addition, when the internal gear 42 starts rotating to adjust the torque i$1, the lock bin 45a and the cam protrusion @4
7, the contact portion of the cam protrusion 47 on the lock bins 45a, 45, etc. is an arcuate surface (not shown), and no matter from which direction the cam protrusion 47 contacts the lock bins 45a, 45b, the cam protrusion 47 will not interfere with the bone 46. Against lock bin 45a = 45
This is prevented by allowing b to be pushed up. Second
In the figure, 70.72 is a washer, 73 is the output shaft 7 and the sun gear 4.
0 (carrier 38) at both ends.

Further, FIG. 9 shows a coupling structure between the case 61 and the motor mounting base 60 in the gear case 6.

That is, on the inner periphery 11 of the rear end of the case 61, there is a locking groove 8 which -i opens to the f&i surface of the case 61 through the groove 86.
7 are provided, and a plurality of protrusions 85 are provided protruding from the motor mounting base 60 to allow assembly of each component into the case 61, fixation of the motor 2 to the motor mounting base 60, and motor 2 output shaft. After press-fitting and fixing the sun gear 31 to the motor mounting base 60, the protrusion 85 on the motor mounting base 60 is
1, and then rotate the motor mount 60 with respect to the case 61 to move the protrusion 85 to the locking groove 87, so that the case 61 and the motor mount 60 are connected in a bayonet manner. It is something that

In this case, when the motor mounting base 60 is rotated for coupling, the sun gear 31 and the planetary gear 32 are engaged at the same time, and in this respect as well, the assembly is easier than when the connection is made using mounting screws. In particular, in the illustrated example, the carrier 34
The tip of the output shaft 20 of the motor 2 is located in the center hole 8 by Flk.
8 is formed, sun gear 31 and i! Since the output shaft 20 enters this center hole 88 before engaging with the star gear 32, it is easy to position the sun gear 31 at the center. The planetary speed variable VC device arranged inside the case 61 has its sun gear 1°35 on the input side and the carrier 34.38 on the output side, and the parts can be assembled into the case 61 in sequence from the opening at the input end. This is partly due to the fact that it is very easy to assemble. Incidentally, since the parts can be assembled into the case 62 sequentially from the input side opening, assembly is easy. Further, the above assembly h1 structure may be used to open the case 61 and the case 62. In any case, the gear case 6 is composed of three parts connected in the ring direction, and the case 61
．． Since all that is required is to assemble the components after attaching each component to the motor mount 62 and the motor 2 to the motor mount 60, good assemblability is exhibited.

In the above embodiment, the second-stage planetary R-structure internal gear 37 is movable in the ring direction and rotatable, and in connecting it to the sun gear 35,
By using the carrier 34 of the first-stage i-leg mechanism that is integrally equipped with the sun gear 35, it has been shown that the size has been reduced by rationalizing the arrangement of parts, but the internal gear 37
may be connected not to the sun gear 35 but to the carrier 38 of the second stage M-leg mechanism. In this case, the engagement protrusion 53 is preferably provided integrally with the internal gear 33, and the internal gear 33 of the first stage planetary fil may be movable and rotatable in the ring direction.

FIG. 11 shows an electric drill driver equipped with the power system assembly described above. In FIG. 11, 9 is a battery pack, 10 is a main body, 11 is a handle, and 2nd is a switch handle. A handle 58 for the 'IIl series is arranged on the upper surface of the main body part 10.

FIG. 2 shows a configuration in which the reduction units 3 are arranged in two stages in series. In this case, by performing the changing operation for each reduction unit 3 individually, a total of 41ffi speed changes can be performed. can.

[Effect of the invention 1 As described above, in the present invention, even when one of the two-stage i-leg mechanisms is directly connected, the speed change by the other planetary mechanism is effective, so that a plurality of gear ratios can be obtained. This makes it possible to obtain a gear ratio with a preferable value for the power tool.

[Brief explanation of drawings]

Fig. 1 is a longitudinal cross-sectional view of the present invention-51 embodiment, Fig. 2 is an exploded perspective view of the same as above, Fig. 3 is a cross-sectional view taken along line X-X in Fig. 1, and Fig. 4 is a cross-sectional view of the The cross-sectional view at Y-Y#a in the figure, !@5 and 6 are longitudinal and cross-sectional views when the internal gear is fixed, and fjST and 8 are the internal gear with the carrier ( 9(a) and 9(b) are an exploded perspective view and a perspective view of the same as above, and FIG. 10 is a perspective view showing the entire power system assembly of the above, FIG. 11 is a perspective view of a power tool equipped with the power system assembly same as above, and FIG. 35 is the sun gear, 32.36 is 'il
1i gear, 33.37 is internal gear, 34.38
is a carrier, 51 is an engagement tooth, 53.54 is an engagement protrusion, 6
0 indicates the motor mounting base, and 61.62 indicates the case. Agent Patent Attorney Ishi 1) Chief 7th 7th “4 8v4 Figure 9

Claims (2)

[Claims] (1) A transmission equipped with a two-stage planetary mechanism consisting of a sun gear, an internal gear, a planetary gear that meshes with both, and a carrier that supports the planetary gear, and the internal gear of either planetary mechanism is moved in the wheel direction. The internal gear is slidably and rotatably rotated around the shaft, and the internal gear is attached to an engaging protrusion provided on the inner surface of the gear case housing the planetary mechanism, and to an engaging protrusion provided on the carrier or sun gear. A power tool characterized by being movable and engageable. (2) The gear case houses a first case equipped with the transmission, a motor mount connected to one end of the first case, and a final stage reduction section.
and a second case connected to the other end of the case, and each planetary mechanism in the transmission has a sun gear on the input side and a carrier on the output side. 2. The power tool according to claim 1, wherein the carrier of the first-stage planetary mechanism integrally equipped with a gear is capable of engaging with an internal gear of the second-stage planetary mechanism.