JPH0957640A - Power tool with transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To allow selecting a shifting mode to well suit the intended use by furnishing a shifting mode changeover means which stops the automatic transmission function of a transmission device. SOLUTION: A speed sensing means SP, for example a feedback generator furnished on a motor, is connected with the input side of a control circuit C, which emits a shift signal to a changeover driving member when the motor speed has sunk in association with increment of the working load so that a shifting operation to enlarge the reduction ratio is performed. The control circuit C is fed with a shifting mode signal given by a shifting mode changeover switch S, a rotating direction signal for regular and reverse rotation caused by a rotating direction changeover rod, and a speed control full signal to indicate that the motor under speed control by a speed control circuit is in the max. output condition.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a power tool with a transmission that automatically shifts according to a load.

[0002]

2. Description of the Related Art Electric screwdrivers and the like have been provided with an automatic shift function in order to improve work efficiency. In a power tool with a transmission device of this type disclosed in Japanese Patent Laid-Open No. 63-151545, if the work load increases, a shift for increasing the reduction ratio from the high-speed rotation and low torque condition up to then is automatically performed. The speed is changed to a low-speed rotation and high-torque state, and work can be performed quickly when the load is low, and when the load becomes high, the reduction ratio automatically increases without adding gear shifting operation. It can be carried out.

[0003]

By the way, in an electric power tool equipped with a transmission having an automatic transmission function as described above, it may be bothersome to change gears during operation and the reduction ratio may be bothersome. May be. The present invention has been made in view of such a point,
An object of the invention is to provide a power tool with a transmission capable of selecting a shift mode according to a work application.

[0004]

DISCLOSURE OF THE INVENTION The present invention, however, provides a gear shift mode switching means for stopping the automatic gear shift function of a gear shifter in an electric tool with a gear shifter that automatically shifts gears by increasing the work load. The present invention is characterized in that it is possible to set the non-automatic shift mode of constant speed by stopping the automatic shift function by the shift mode switching means.

The non-automatic shift mode at this time may be a low speed mode having a large reduction ratio or a high speed mode having a small reduction ratio, but a low speed mode having a large reduction ratio, It may be possible to switch between two types of high speed mode in which the reduction ratio is small.

[0006]

BEST MODE FOR CARRYING OUT THE INVENTION An example of an embodiment of the present invention will be described below in the case of an electric power tool which is an electric drill driver shown in the drawings. First, the transmission in the speed reduction mechanism section up to the output shaft 5 including the motor 6 that is power and the chuck 50 that is the output section will be described. As shown in FIGS. 4 to 6, one end opening of the gear case 1 is opened. On the output shaft 60 of the motor 6 arranged on the side, two sun gears 1 having different numbers of teeth are provided.
1, 12 are fixed, and a plurality of planet gears 21, 22 are meshed with the sun gears 11, 12 arranged in the axial direction, and three sun gears 21, 22 are meshed with each other in the illustrated example. Both planetary gears 21 and 22 having different numbers of teeth are supported by the carrier 4, and the planetary gear 21 is supported around the sun gear 11 at equal intervals and the planetary gear 22 is supported around the sun gear 12 at equal intervals. The two planetary gears 21 and 22 perform the same revolution, though they rotate individually.

The planet gear 21 is engaged with the ring gear 31 arranged concentrically with the output shaft 60, and the ring gear 32 also arranged concentrically with the output shaft 60 is engaged with the planet gear 22. Of these two ring gears 31 and 32 arranged in the axial direction, the ring gear 31 has a plurality of engaging projections 35 formed on the outer peripheral surface thereof at equal intervals in the circumferential direction, and the ring gear 31 is free from the gear case 1. It is said to be freely rotatable. The ring gear 32 is also freely rotatable with respect to the gear case 1, and the ring gear 32 also serves as the inner race 331 of the one-way clutch 33 having the gear case 1 as the outer race 330. ing.

The one-way clutch 33 here is
As described above, the gear case 1 is the outer race 330, the ring gear 32 is the inner race 331,
A freewheel type formed by arranging balls 332 in a wedge-shaped space formed between 0 and 331,
In addition to having two types of wedge-shaped spaces with different narrowing directions,
A drive piece 77 projecting from the forward / reverse switching ring 76 is located between the two kinds of wedge-shaped spaces, and the forward / reverse switching ring 76 is rotated with respect to the gear case 1 so as to be positioned on both sides of the drive piece 77. Depending on which one of the pair of balls 332, 332 is pressed by the drive piece 77, the rotatable direction of the ring gear 32 which is the inner race 331 can be switched.

That is, when the driving piece 77 pushes the ball 332 on one side into the wider side of the wedge-shaped space as shown in FIG. 7, the other ball 332 is positioned in the narrow portion of the wedge-shaped space by being biased by the spring 333. In this state, rotation of the ring gear 32 (inner race 331) in the direction of arrow A in the figure is possible, but rotation of the ring gear 32 in the direction of arrow B in the figure is blocked. When the driving piece 77 pushes the ball 332 on the right side in the figure to the right side in the figure, on the contrary, the ring gear 32 (inner race 331) in the direction of the arrow B in the figure can be rotated and the ring gear 32 in the direction of the arrow A. Rotation is blocked.

In the gear case 1, in addition to the planetary mechanism, the forward / reverse switching ring 76 and the one-way clutch 33, a locking ring 70 is arranged. The locking ring 70, which is slidable in the axial direction, is provided with a protrusion 71 that engages with the engaging protrusion 35 on the outer peripheral surface of the ring gear 31 when moved in one direction. The rotation of the ring gear 31 is prevented, and the rotation of the ring gear 31 is allowed when the engagement between the engagement protrusion 35 and the protrusion 71 is released by the sliding. The axial slide of the locking ring 70 causes the switching drive member 7 such as a solenoid,
The lever 65 is pivotally supported by the shaft 66 on the outer surface of the gear case 1, and has one end connected to the switching drive member 7 and the other end connected to the connecting shaft 72 protruding from the outer peripheral surface of the locking ring 70.

The carrier 4 supporting the planetary gears 21 and 22 is integrally provided with a sun gear 41, and the rotation of the sun gear 41 supports the planetary gear 42 meshing with the sun gear 41 and the ring gear 43. The rotation of the carrier 44 is transmitted to the output shaft 5 through the auto-lock mechanism 55. The auto-lock mechanism 55 here automatically locks the output shaft 5 with respect to the gear case 16 when the rotation of the motor 6 is stopped, and automatically releases the lock when the motor 6 is rotated. However, description of this point will be omitted. Further, the ring gear 43 is also allowed to freely rotate, and the ball 48 is engaged with the ring gear 43 by the spring pressure of the clutch spring 47, so that the output shaft 5 and the sun gear 41 are connected to each other when the load torque exceeds a predetermined value. It constitutes a torque limiter that disconnects
A description of this point will also be omitted. In the figure, 13 is the forward / reverse switching ring 76 while ensuring the operation space of the forward / reverse switching ring 76.
Is provided to eliminate the sliding resistance between the ring gear 32 and the ring gear 32 and serves as the thrust receiving surface of the ring gear 32. The lid member 10 has one end of the gear case 1 closed. It is formed integrally.

Now, as shown in FIG. 6 (a), the locking ring 7
When 0 is blocking the rotation of the ring gear 31 and the one-way clutch 33 is set so that the ring gear 32 can rotate in the direction shown by the arrow in the figure, if the motor 6 is rotated, the rotation output will be , Is transmitted to the carrier 4 through the planetary gear 21 that meshes with the ring gear 31 whose rotation is blocked. At this time, the ring gear 32 is in one direction, and this idling is the direction in which the rotation shown by the arrow in the figure is permitted.

Then, the switching drive member 7 is activated in response to the detection of the increase in the load, and the locking ring 7 is moved as shown in FIG. 6 (b).
When 0 moves to release the engagement between the engagement projection 35 and the projection 71, the ring gear 31 becomes free, and the stop of the carrier 4 connected to the load meshes with the sun gears 11 and 12 to the planetary gears 21 and 22. Rotation of the ring gear 31,3
2, the ring gear 32 at this time rotates in the opposite direction to the idle rotation, that is, the rotation is blocked by the one-way clutch 33. Power is transmitted to the carrier 4 and the output shaft 5 through the planetary gear 22 that meshes with the gear 32.

Since the number of teeth of the sun gear 12 is smaller than the number of teeth of the sun gear 11 and the number of teeth of the planetary gear 22 is larger than the number of teeth of the planetary gear 21, the high speed rotation low torque state is changed to the low speed rotation high torque state. It has been switched. Moreover, in this gear shifting, the one-way clutch 33 is used to stop the rotation of the ring gear 32, so that only the locking ring 70 is separated from the locking projection 35 of the ring gear 31, and the collision is performed to prevent the rotation of the ring gear 32. Therefore, smooth and noise-free gear shifting is performed despite the fact that there is no member that causes the occurrence of gear shifting and therefore the gear shifting is in operation. The return from the low-speed rotation high-torque state to the high-speed rotation low-torque state is performed by the return of the switching drive member 7, and this shift is performed when the motor 6 is stopped or the motor 6 is started.

By rotating the forward / reverse switching ring 76,
When the rotation direction of the one-way clutch 33 is reversed and the rotation direction of the motor 6 is reversed,
Power is transmitted to the carrier 4 through the planetary gear 21 that meshes with the ring gear 31 whose rotation is stopped by the locking ring 70. At this time, the ring gear 32 idles in the rotatable direction of the one-way clutch 33, which increases the load. When the switching drive member 7 is actuated and the ring gear 31 becomes free upon detection, power is transmitted to the carrier 4 through the ring gear 32 whose rotation is blocked by the one-way clutch 33 and the planetary gear 22 meshing with the ring gear 32. Although there is only one one-way clutch 33, the rotation blocking direction can be switched so that the same operation can be obtained in the forward rotation and the reverse rotation required for the electric drill driver. However, this is only done mechanically, and as will be described later, when the motor 6 rotates in the reverse direction, the switching drive member 7 is not actually operated in accordance with the work load to automatically shift gears.
The operation of the forward / reverse switching ring 76 in the illustrated example is performed by the rotation direction switching rod 8 shown in FIG.
1 and a switching lever 90, one end of which is engaged with the rotation direction switching rod 8 and the other end of which is engaged with the forward / reverse switching ring 76. The rotation direction switching rod 8 here is
It also works in conjunction with the switch unit SW shown in FIG. 3, so that the rotation direction of the motor 6 is switched at the same time.

Next, the control circuit C for operating the switching drive member 7 will be described. The control circuit C formed by a microcomputer and a logic IC includes a motor 6
A speed detection means SP such as a feedback generator (FG) provided at the input side is connected to the input side, and outputs a shift signal to the switching drive member 7 when the rotation speed of the motor 6 decreases as the work load increases. The speed change operation for increasing the reduction ratio is performed by the control circuit C.
In addition to the rotation speed signal, a speed change mode signal from a speed change mode switch S, a rotation direction signal for forward rotation and a reverse rotation due to the rotation direction change rod 8, and a speed control circuit perform speed control. A speed control full signal indicating whether or not the motor 6 is in the maximum output state is input. The shift signal is output by referring to the shift signal, the switching signal, and the speed control full signal.

That is, the speed change mode switch S is
The switching handle 95 shown in FIG. 3 is used to switch between the automatic shifting mode and the mode in which automatic shifting is not performed.
The operation is to switch between both modes.
When the automatic shift mode is not set, the control circuit C described above is used.
Does not output a shift signal according to an increase in work load, and keeps the reduction ratio constant. Note that the flowchart shown in FIG. 1 shows that the shift signal is immediately output at the start of work to perform the work from beginning to end in the high torque low speed rotation state in which the reduction ratio is increased. As shown in
The low torque and high speed rotation state may be continued until the work is completed without outputting the shift signal.

The speed control circuit has a trigger switch handle 9 in the switch unit SW shown in FIG.
The feedback control of the rotation speed of the motor 6 is performed while referring to the speed detected by the speed detecting means SP so that the rotation speed of the motor 6 becomes higher as the amount of pulling increases. When 9 is pulled to the maximum, the above speed control full signal is input to the control circuit C, and the control circuit C outputs the speed change signal according to the decrease in the rotation speed of the motor 6 to the speed. It should be performed only when the control full signal is input, that is, when the motor 6 is rotating at the maximum output. When the maximum output is not reached, the rotation speed of the motor 6 decreases due to the increase in load. Even if there is, the shift signal is not output.

Furthermore, the direction of the current flowing through the motor 6 is switched by switching the rotation direction of the motor 6 by the above-described rotation direction switching rod 8 and the switch unit SW. The voltage is monitored, and when the motor 6 is in the normal rotation state, a shift signal is output according to the decrease in the rotation speed of the motor 6, but when the motor 6 is in the reverse rotation state, the rotation of the motor 6 due to the increase in the load occurs. Even if the number is reduced, the shift signal is not output.

That is, in this electric power tool, the motor 6 is in the normal rotation state, the shift mode is set to the automatic shift mode, and the trigger switch handle 9 is further provided.
Is automatically pulled only when the motor 6 is rotated at the maximum output and the work load increases, and when the above three conditions are not satisfied, the work load increases. Even if it does not automatically shift.

When automatically shifting from the high speed rotation low torque state to the low speed rotation high torque state, the operation is performed in the high speed rotation low torque state even after the work load is large from the beginning, and then the low speed rotation high torque state is entered. . In this case, the shift shock may be troublesome, and as shown in FIG.
When the work load is high in the high-speed rotation low-torque state H, the power consumption I _H is extremely large, so that there are many problems in the case where the power source of the motor 6 is obtained from the battery. Thus when a and keep the non-automatic shift mode operating at low speed and high torque state L from the beginning, only a small power consumption I _L on may work efficiency.

The embodiment shown in FIG. 11 has a switching handle 95.
It is assumed that the shift mode changeover switch S can be switched between three modes, an automatic shift mode, a low speed mode and a high speed mode. The torque state is set, and when the high speed mode is set, the gear is not changed and the high speed rotation and low torque state are set, and these states are maintained until the end of the work.

[0023]

As described above, according to the present invention, the shift mode switching means for stopping the automatic shift function of the transmission is provided, and the automatic shift function is stopped by the shift mode switching means to perform the non-automatic shift of constant speed. It can be set to the mode, and you can enjoy the advantages of automatic shifting, and if it is bothersome to switch gears by automatic shifting during work, or if it is rather unusable on the contrary. This can be dealt with by setting the non-automatic shift mode, and the shift mode can be selected according to the work application.

The non-automatic shift mode at this time may be a low speed mode having a large reduction ratio or a high speed mode having a small reduction ratio, but a low speed mode having a large reduction ratio, If it is possible to switch between two types of high speed mode with a small reduction ratio, it is possible to cope with any work application in which the non-automatic shift mode is preferable.

[Brief description of drawings]

FIG. 1 is a flowchart showing an operation in an example of an embodiment of the present invention.

FIG. 2 is a block circuit diagram of the above.

FIG. 3 is a longitudinal sectional view of the same.

FIG. 4 is a vertical cross-sectional view of the gear case portion of the above.

FIG. 5 is a transverse sectional view of the gear case portion of the above.

FIG. 6 is a perspective view showing a shift operation of the above, wherein (a) is a perspective view showing a state before a shift, and (b) is a perspective view showing a state after a shift.

FIG. 7 is an explanatory diagram of a rotation direction switching portion of the above one-way clutch.

FIG. 8 is a sectional view showing a rotation direction switching operation unit of the above.

FIG. 9 is a characteristic diagram of motor current, rotation speed, and torque of the same as above.

FIG. 10 is a flowchart showing an operation in another example.

FIG. 11 is a flowchart showing an operation in another example.

[Explanation of symbols]

 6 Motor C Control circuit S Gear change mode switch

Claims (4)

[Claims] 1. A power tool with a transmission that automatically shifts a reduction gear ratio by increasing a work load, the transmission including a shift mode switching means for stopping an automatic shift function of the transmission. Power tool with device. 2. The electric tool with a transmission according to claim 1, wherein the non-automatic shift mode is a low speed mode having a large reduction ratio. 3. The power tool with a transmission according to claim 1, wherein the non-automatic shift mode is a high speed mode with a small reduction ratio. 4. The non-automatic shift mode is provided so as to be switchable between a low speed mode having a large reduction ratio and a high speed mode having a small reduction ratio. Power tool with transmission.