WO2012114815A1

WO2012114815A1 - Power tool

Info

Publication number: WO2012114815A1
Application number: PCT/JP2012/051545
Authority: WO
Inventors: 将利渥美; 賢一郎稲垣; 直有村; 博之海藏; 山田　穣
Original assignee: パナソニックＥｓパワーツール株式会社
Priority date: 2011-02-22
Filing date: 2012-01-25
Publication date: 2012-08-30
Also published as: JP5662829B2; JP2012171047A

Abstract

A power tool includes: a motor; a speed reduction mechanism (2) that reduces the speed of and transmits the rotative power of the motor (1); and a speed reduction ratio switching means that switches the speed reduction ratio of the mechanism (2). The mechanism (2) includes: a switching member (7) that is slidable in the axial direction of the mechanism; and a gear member (5) that is capable of engaging with the member (7). The switching means includes: a speed change actuator (6) that slides the member (7); a drive adjustment unit (61) that adjusts the driving of the actuator (6); a switch control unit (63) that reduces the relative rotation speeds of the members (7, 5) when the speed reduction ratio is switched; and an actuator control unit (64) that controls the actuator (6). The control unit (64) controls the adjustment unit (61) so that the slide amount per unit of time of the member (7) remains constant.

Description

Electric tool

The present invention relates to an electric tool provided with a changeable reduction ratio.

In a power tool provided with a speed reduction mechanism section, there is a structure for switching the engagement state by sliding a switching member such as a ring gear constituting the planetary speed reduction mechanism in the axial direction as a structure for switching the speed reduction ratio of the speed reduction mechanism section. .

For example, in the electric tool described in Japanese Patent Application Publication Nos. 2009-56590 and 2009-78349, the switching operation of the ring gear is automatically performed using a solenoid. In this conventional electric tool, in order to suppress the impact when the switching member engages with another gear member, the rotation of the motor is stopped or reduced when the solenoid is started.

In the above-described conventional power tool, when a change occurs in the current of the motor serving as the drive source, the control unit that detects this changes the start of the solenoid and the rotation stop of the motor according to the set timing. Is running. Specifically, first, the rotation of the motor for suppressing the impact is reliably stopped, and then the solenoid is activated to take measures to suppress the impact at the time of engagement as much as possible.

By the way, there is a certain amount of time between the timing at which the switching member is actually engaged with the predetermined gear member and the timing at which the motor is decelerated and the motor actually stops rotating as intended. There is variation. In the conventional electric tool described above, since the solenoid is started after the motor rotation is reliably stopped, it is difficult to complete the reduction ratio change in a short time.

That is, the conventional electric tool as described above is insufficient to suppress the impact of engagement when changing the reduction ratio and to complete the reduction ratio change smoothly in a short time. Met.

In addition, when the switching member slides, the changeover of the battery power source of the power tool, the wear of the gear member, the shaft misalignment, the increase of the clearance between the gear members, etc., before the switching member reaches the predetermined target position. The slide may stop. In this case, since the switching member is displaced from the predetermined target position, the engagement between the switching member and the gear member becomes insufficient, and unexpected shifts due to insufficient engagement, wear of the engagement parts, In some cases, it could cause damage.

However, in the conventional electric tool as described above, the control unit does not include control for avoiding insufficient engagement between the switching member and the gear member due to insufficient sliding amount of the switching member.

It is an object of the present invention to suppress the impact of engagement when changing the reduction ratio, to complete the change of the reduction ratio smoothly in a short time, and when the reduction ratio is changed, the sliding amount of the switching member is insufficient. It is to make it difficult.

The present invention includes a motor (1) as a drive source, a speed reduction mechanism (2) configured to reduce the rotational power of the motor (1) and transmit the reduced rotational power, and the speed reduction A reduction ratio switching means configured to switch the reduction ratio of the mechanism section (2). The deceleration mechanism section (2) includes a switching member (7) that includes a shaft and is slidable in the axial direction, and the switching member (7) according to a sliding position of the switching member (7) in the axial direction. A gear member (5) capable of switching between an engaged state and a non-engaged state, and configured to switch the reduction ratio through the switching member (7) and the gear member (5). The reduction ratio switching means is configured to adjust the drive of the speed change actuator (6) and the speed change actuator (6) configured to slide the switch member (7) in the axial direction. A drive adjustment unit (65), a switching control unit (63) configured to reduce a relative rotational speed of the switching member (7) and the gear member (5) when the reduction ratio is switched, and the reduction ratio An actuator control unit (64) configured to control the shift actuator (6) at the time of switching. The actuator control unit (64) is configured to control the drive adjustment unit (65) so as to keep the sliding amount per time of the switching member (7) by the speed change actuator (6) constant. .

In one embodiment, the reduction ratio switching means further includes an information detection unit (67) configured to detect input / output information of the speed change actuator (6), and the actuator control unit (64) includes: The drive adjustment unit (65) is controlled according to the detection result of the information detection unit (67).

In one embodiment, the actuator control section (64) causes the drive adjustment section (65) to maintain a constant supply voltage to the speed change actuator (64), thereby increasing the moving speed of the switching member (7). It is configured to be held constant.

In one embodiment, the information detection unit (67) is configured to detect a voltage applied to the shift actuator (6) as the input / output information before the shift actuator (6) is activated. The The drive adjusting unit (65) is configured to adjust the power supplied to the speed change actuator (6) according to the detection result of the information detecting unit (67).

In one embodiment, the information detection unit (67) is configured to detect a current value flowing through the shift actuator (6) when the shift actuator (6) is driven as the input / output information. The drive adjusting unit (65) is configured to adjust the power supplied to the speed change actuator (6) according to the detection result of the information detecting unit (67).

In one embodiment, the reduction ratio switching means further includes a slide position detection unit (68) configured to detect the slide position of the switching member (7). The actuator control section (64) adjusts the power supplied to the speed change actuator (6) according to the detection result of the slide position detection section (68) and the detection result of the information detection section (67). Configured.

In one embodiment, the information detection unit (67) is configured to detect a driving time and a current value of the shift actuator (6) as the input / output information.

In one embodiment, the information detection unit (67) is configured to detect a voltage value and a current value of the shift actuator (6) as the input / output information.

In one embodiment, the information detection unit (67) is configured to detect an operation speed and a current value of the shift actuator (6) as the input / output information.

In one embodiment, the actuator control unit (64) is configured to control the sliding amount per time to be different for each sliding direction of the switching member (7).

The present invention suppresses the impact of engagement when changing the reduction ratio and can complete the reduction ratio change smoothly in a short time, and when the reduction ratio is changed, the sliding amount of the switching member is insufficient. There is an effect that it can be made difficult.

Preferred embodiments of the invention are described in further detail. Other features and advantages of the present invention will be better understood with reference to the following detailed description and accompanying drawings.
It is principal part explanatory drawing of the electric tool of Embodiment 1 of this invention. It is a sectional side view of an electric tool same as the above. It is an internal side view of an electric tool same as the above. It is a back sectional view of an electric tool same as the above. It is a disassembled perspective view of the deceleration mechanism part of an electric tool same as the above. FIG. 6A is a side sectional view, and FIG. 6B is a side view, showing a first speed state of the speed reduction mechanism portion. It is a sectional side view which shows the state in the middle of switching of 1st speed and 2nd speed of the deceleration mechanism part same as the above. FIG. 8A is a side sectional view, and FIG. 8B is a side view, showing a second speed state of the speed reduction mechanism portion. It is a sectional side view which shows the state in the middle of the 2nd speed and 3rd speed switching of the deceleration mechanism part same as the above. FIG. 10A is a side sectional view, and FIG. 10B is a side view, showing a state of the third speed of the reduction mechanism unit. It is principal part explanatory drawing of the electric tool of Embodiment 2 of this invention. It is explanatory drawing of adjustment control of the supply voltage of the electric tool of Embodiment 3 of this invention. It is explanatory drawing of the stationary current estimation of the electric tool of Embodiment 4 of this invention. It is explanatory drawing of adjustment control of the supply voltage according to a stationary current estimation result same as the above. It is explanatory drawing of the load torque estimation of the electric tool of Embodiment 6 of this invention. It is explanatory drawing of adjustment control of the supply voltage according to the load torque of the electric tool of Embodiment 7 of this invention. It is explanatory drawing of adjustment control of the supply voltage according to the load torque of the electric tool of Embodiment 8 of this invention.

(Embodiment 1)
2 to 4 show Embodiment 1 of the electric power tool of the present invention. The electric tool of the present embodiment includes a motor (main motor) 1 that is a drive source, a speed reduction mechanism unit 2, and a drive transmission unit 3. The reduction mechanism unit 2 includes a switching member 7 and is configured to reduce the rotational power of the motor 1 and transmit the reduced rotational power. In the present embodiment, the reduced rotational power is transmitted to the drive transmission unit 3. The drive transmission unit 3 is configured to transmit the rotational power transmitted through the speed reduction mechanism unit 2 to the output shaft 4. In the illustrated example, a bit is attached to the output shaft 4 via a chuck. Here, the switching member of the present invention has a shaft (hereinafter also referred to as “main shaft”) and is configured to slide in the direction of the main shaft. In the present embodiment, the switching member 7 has one common axis and is configured to slide in the direction of the common axis. Specifically, the motor 1, the speed reduction mechanism unit 2, and the drive transmission unit 3 are accommodated in the body housing 101 such that their respective axes are arranged on an extension line of the output shaft 4. In other words, each of the motor 1, the speed reduction mechanism unit 2, the drive transmission unit 3, and the output shaft 4 has one common axis CA (see FIG. 5) that is coaxial with its own axis.

A grip part housing (grip) 102 extends from the body housing 101, and the main body housing 100 of the electric tool is composed of the body housing 101 and the grip part housing 102. A trigger switch 103 is retractably provided in the grip part housing 102. Furthermore, a power cord connected to an external power source and a power source unit 70 such as a battery pack that can be detached from the grip unit housing 102 (see FIG. 1 and the like) are provided at the extended distal end of the grip unit housing 102.

Further, in the body housing 101, as shown in FIG. 1, the speed change actuator 6 is disposed in the axial direction 6A of the speed change actuator 6 with respect to the main shaft (the common axis CA) such as the motor 1 and the speed reduction mechanism 2. Are housed in parallel. The speed change actuator 6 is a rotary actuator having a dedicated motor (sub motor) 50 as a drive source, and the switching member 7 included in the speed reduction mechanism 2 is moved in the axis (main axis) direction via the speed change cam plate 8. It is configured to slide and switch the reduction ratio. This will be described in detail later.

5 to 10 show the structure of the speed reduction mechanism 2 and the like in more detail. The speed reduction mechanism unit 2 of the present embodiment accommodates a three-stage planetary speed reduction mechanism in the gear case 9, and the speed reduction mechanism part 2 is switched by switching between the deceleration state and the non-deceleration state of the planetary speed reduction mechanism of each stage. Change the overall reduction ratio. In the following description, the first, second, and third stage planetary speed reducing mechanisms will be described in order from the side closer to the motor 1.

As shown in FIG. 5, the first stage (first) planetary reduction mechanism 2 _1, the sun gear 10 which is rotationally driven around the axis by the rotation power from the motor 1 (see FIG. 6A), the sun gear 10 And a plurality of planetary gears 11 that mesh with each other, and a ring gear 12 that meshes with each planetary gear 11. The planetary gear 11 is positioned so as to surround the sun gear 10. The ring gear 12 is positioned so as to surround the plurality of planetary gears 11. Planetary reduction mechanism 2 ₁ of the first stage further comprises a carrier 14 and a plurality of carrier pins 13. The plurality of planetary gears 11 are rotatably connected to the carrier 14 via a plurality of carrier pins 13 respectively.

The second stage (second) planetary reduction mechanism 2 _2, the second-stage sun gear 20 that is coupled to the sun gear 10 of the first stage (see FIG. 6A), a plurality of planetary gears meshing with the sun gear 20 21. The first-stage ring gear 12 is arranged to mesh with the plurality of planetary gears 21 and is shared with the second-stage planetary reduction mechanism 22. The planetary gear 21 is positioned so as to surround the sun gear 20. Planetary reduction mechanism 2 ₂ of the second stage further comprises a carrier 24 and a plurality of carrier pins 23. The plurality of planetary gears 21 are rotatably connected to the carrier 24 via a plurality of carrier pins 23, respectively. The tip of the carrier pin 23 is connected to the first stage carrier 14.

Ring gear 12, or functions as a member for forming the planetary reduction mechanism 2 ₁ of the first stage, it works as a member for forming a second-stage planetary reduction mechanism 2 _2, depending on the slide position It is a structure that can be selected alternatively. That is, the ring gear 12 meshes with the first stage planetary gear 11 when in the sliding position on the motor 1 side, and meshes with the second stage planetary gear 21 when in the sliding position on the output shaft 4 side.

In the following text, the motor 1 side is simply referred to as “input side” and the output shaft 4 side is simply referred to as “output side”.

A guide portion 15 (see FIG. 7) is provided on the inner peripheral surface of the gear case 9 so that the ring gear 12 is slidable and non-rotatable in the axial (main shaft) direction. While being guided by 15, the slide movement in the direction of the axis (main axis) is performed.

The third stage (third) planetary reduction mechanism 2 ₃ includes a sun gear 30 of the third stage is coupled to the carrier 24 of the second stage, a plurality of planetary gears 31 meshing with the sun gear 30, a plurality of these A ring gear 32 that meshes with the planetary gear 31 is provided. The planetary gear 31 is positioned so as to surround the sun gear 30. The third stage planetary reduction mechanism 2 ₃ further includes a carrier 34 and a plurality of carrier pins 33. The plurality of planetary gears 31 are rotatably connected to the carrier 34 via a plurality of carrier pins 33, respectively.

The ring gear 32 is slidably and rotatably arranged in the axial direction with respect to the gear case 9. When the ring gear 32 is in the input-side slide position, the ring gear 32 meshes with the outer peripheral edge of the second stage carrier 24. When the ring gear 32 is in the slide position on the output side, the ring gear 32 meshes with an engagement tooth portion 40 (see FIG. 6A) formed integrally with the gear case 9. Further, the ring gear 32 meshes with the planetary gear 31 at any sliding position.

Planetary reduction mechanism 2 ₃ of these three stages is connected to the shaft (main shaft) direction. That is, the first to third sun gears 10, 20, and 30 are arranged side by side in a straight line in the axial direction (main axis), and the two ring gears 12 and 32 positioned so as to surround them are also in the axial (main axis) direction. Are arranged side by side.

The ring gears 12 and 32 are independently slidable in the axial direction, and the reduction ratio is switched corresponding to the sliding position, and the rotation output of the output shaft 4 is changed to the first speed, the second speed, and the third speed. Thus, in the present embodiment, the ring gears 12 and 32 form the switching member 7 that is slidable in the axial (main axis) direction. In this embodiment, the first speed is the state with the smallest reduction ratio, the second speed is the state with the larger reduction ratio than the first speed, the third speed is the state with the larger reduction ratio than the first and second speeds (that is, the smallest reduction ratio). Big state). The switching member of the present invention is not limited to the ring gears 12 and 32. The switching member of the present invention may be configured to include at least one ring gear (for example, ring gear 12).

6 shows the state of the first speed, FIG. 7 shows the state during the switching between the first speed and the second speed, FIG. 8 shows the state of the second speed, FIG. 9 shows the state during the switching between the second speed and the third speed, FIG. Shows the state of the third speed.

In the speed reduction mechanism section 2 at the first speed in FIG. 6, one ring gear 12 forming the switching member 7 is in the input side position, and the other ring gear 32 forming the switching member 7 is also in the input side position. Therefore, only the planetary reduction mechanism 2 ₁ of the first stage is the deceleration state.

In the second speed reduction mechanism portion 2 in FIG. 8, one ring gear 12 forming the switching member 7 is at the output side position, and the other ring gear 32 forming the switching member 7 is also at the input side position. Therefore, only the second stage planetary speed reduction mechanism 2 ₂ is in a deceleration state.

Here, in the first-stage planetary reduction mechanism 2 ₁ and second-stage planetary speed reduction mechanism 2 ₂ 2/5 stage is made different for dimensions of each member so that ratio speed reduction becomes large. Therefore, in the case of the second speed, the reduction ratio is larger than that of the first speed, and the rotation speed of the output shaft 4 is reduced.

In the speed reduction mechanism portion 2 at the third speed in FIG. 10, one ring gear 12 forming the switching member 7 is at the output side position, and the other ring gear 32 forming the switching member 7 is also at the output side position. Therefore, both the second-stage planetary speed reduction mechanism 2 ₂ and the third-stage planetary speed reduction mechanism 2 ₃ are in a decelerating state.

Both the sliding positions of the two ring gears 12 and 32 forming the switching member 7 are determined according to the rotational position of the transmission cam plate 8. The transmission cam plate 8 is a plate having an arcuate cross section along the outer peripheral surface of the cylindrical gear case 9, and is mounted so as to be rotatable around the central axis of the gear case 9.

The transmission cam plate 8 has two

cam grooves

41 and 42 arranged side by side in the axial direction (main axis). The input side cam groove 41 is a through groove having a polygonal line shape corresponding to the sliding movement of the ring gear 12. The tip of the speed change pin 45 inserted through the cam groove 41 is inserted into the gear case 9 through a guide groove 48 (see FIG. 5) penetrating the gear case 9 and is engaged with the concave groove on the outer peripheral surface of the ring gear 12. Match. The guide groove 48 is formed in parallel with the axis (main axis) direction of the speed reduction mechanism unit 2.

The output side cam groove 42 is a through groove having a polygonal line shape corresponding to the sliding movement of the ring gear 32. The tip of the speed change pin 46 inserted into the cam groove 42 is inserted into the gear case 9 through a guide groove 49 (see FIG. 5) penetrating the gear case 9, and is engaged with the concave groove on the outer peripheral surface of the ring gear 32. Match. The guide groove 49 is formed in parallel with the axis (main axis) direction of the speed reduction mechanism portion 2 and is formed in a straight line with the other guide groove 48.

The speed change cam plate 8 has a gear portion 47 that meshes with the rotary speed change actuator 6 at its circumferential end. The speed change actuator 6 has a dedicated motor 50, a speed reduction mechanism portion 51 that reduces and transmits the rotational power of the motor 50, and an output portion 52 that is rotationally driven by the rotational power transmitted through the speed reduction mechanism portion 51. . That is, the speed change actuator 6 is configured to slide the switching member 7 in the axial direction via the speed change cam plate 8.

As described above, in the electric power tool of the present embodiment, the speed reduction mechanism unit 2 includes the switching member 7 that is slidable in the axial (main axis) direction, and the switching member 7 according to the sliding position of the switching member 7 in the axial direction. The gear member 5 that can be switched between the engaged state and the non-engaged state is formed.

The switching member 7 is the ring gears 12 and 32 as described above. The gear member 5 here is the first stage planetary gear 11 and the second stage planetary gear 21 for the ring gear 12, and the second stage carrier 24 for the ring gear 32. It is the denture part 40. FIG. The speed reduction ratio of the entire speed reduction mechanism 2 is switched according to the engagement state and the non-engagement state of the switching member 7 and the gear member 5.

In short, the first planetary reduction mechanism 2 ₁ a ring gear 12 that is shared by the second planetary reduction mechanism 2 ₂ (first switching member) is provided so as to slide along the main axis direction, the first speed position (FIG. 6 in), while meshing with the first planetary reduction mechanism 2 ₁ of the first gear set (planet gear 11), the second speed position (FIG. 8), a second planetary reduction mechanism 2 ₂ of the second gear set (planetary gears 21). On the other hand, the ring gear 32 (second switching member) is provided so as to slide along the main axis direction, the first speed position and a second speed position, the carrier 24 and the third planetary reduction mechanism 2 ₃ of the third gear set ( While rotating in mesh with the planetary gear 31), at the third speed position (FIG. 8), rotation is prohibited by meshing with the third gear set and the engaging tooth portion 40.

At the first speed position, the rotation of the sun gear 10 is decelerated by the planetary gear 11 and the ring gear 12, and the carrier 14 rotates through the planetary gear 11 that rotates in the ring gear 12 that is prohibited from rotating in the gear case 9. Since the carrier 24 is connected to the carrier 14 via the carrier pin 23, and the ring gear 32 that meshes with the planetary gear 31 meshes with the carrier 24, the rotation of the sun gear 10 decelerated with the smallest reduction ratio is 14 and 24 are transmitted to the sun gear 30 and the ring gear 32. As a result, the entire 3-stage planetary reduction mechanism 2 ₃ rotates the smallest reduction ratio in synchronism with the carrier 14 (24 well).

At the 2nd speed position, the rotation of the sun gear 20 is decelerated by the planetary gear 21 and the ring gear 12, and the carrier 24 (also 14) is transmitted through the planetary gear 21 that rotates in the ring gear 12 that is prohibited from rotating in the gear case 9. Rotate. Thus, rotation of the decelerated sun gear 20 with a small reduction ratio for the second is transmitted to the sun gear 30 and ring gear 32 via the carrier 24, (also carrier 14) planetary reduction mechanism 2 ₃ entire third stage However, it rotates at the second smallest reduction ratio in synchronization with the carrier 24.

At the 3rd speed position, the rotation of the sun gear 20 is decelerated by the planetary gear 21 and the ring gear 12, the carrier 24 (also 14) rotates, and the sun gear 30 rotates in synchronization with the carrier 24. The rotation of the sun gear 30 is decelerated by the planetary gear 31 and the ring gear 32, and the carrier 34 rotates through the planetary gear 31 that rotates in the ring gear 32 that is prohibited from rotating in the gear case 9. That is, the rotation of the carrier 34 is decelerated at the largest reduction ratio. By the way, in each of the 1st speed position, the 2nd speed position, and the 3rd speed position, the rotation of the carrier 34 is transmitted to the output shaft 4 from the gear formed on the output side surface of the carrier 34 shown in FIG. Is done.

Further, as schematically shown in FIG. 1, the electric tool of the present embodiment includes a control unit 62 configured to control the motor 1 and the actuator 6, and a motor drive configured to drive the motor 1. And an actuator driving unit 66 configured to drive the speed change actuator 6. Power is supplied from the power supply unit 70 to the control unit 62, the motor drive unit 65, and the actuator drive unit 66.

The motor drive unit 65 is configured to drive the motor 1 and change the rotational power of the motor 1 under the control of the control unit 62, and to be configured to adjust the rotational power of the motor 1. Also serves as a drive adjustment unit. The actuator drive unit 66 is configured to drive the speed change actuator 6 (motor 50) and adjust the drive of the speed change actuator 6 under the control of the control unit 62, and to drive the speed change actuator 6 side. The function as 61 is included.

The electric power tool of the present embodiment includes an information detection unit 67 configured to detect input / output information of the speed change actuator 6 and a drive state detection unit 60 configured to detect the drive state of the motor 1. And a slide position detector 68 configured to detect the slide position of the switching member 7.

The driving state detection unit 60 detects the driving state of the motor 1 by detecting at least one of the current value flowing through the motor 1 and the rotation speed of the motor 1, and inputs the detection result to the control unit 62. The information detection unit 67 detects the value of the supply voltage applied to the actuator driving unit 66 (voltage value of the supply power), thereby moving the switching member 7 (that is, the sliding speed of each of the ring gears 12 and 32). And the detection result is input to the control unit 62. The slide position detection unit 68 detects the rotational position of the speed change cam plate 8 linked to the switching member 7 with respect to the gear case 9 to indirectly detect the position of the switching member 7 (that is, the sliding position of each of the ring gears 12 and 32). ) And the detection result is input to the control unit 62. The slide position detection unit 68 may be a non-contact type displacement detection sensor, or may be a contact type that directly contacts the speed change cam plate 8.

The control unit 62 activates the speed change actuator 6 in the actuator driving unit 66 and slides the switching member 7 in accordance with the driving state (load) of the motor 1 detected by the driving state detection unit 60, thereby reducing the speed reduction mechanism. It is comprised so that the reduction ratio of the part 2 may be changed.

That is, in the electric tool of the present embodiment, using the speed change actuator 6, the actuator driving unit 66, the driving state detecting unit 60, the slide position detecting unit 68, the information detecting unit 67, and the control unit 62, It constitutes a reduction ratio switching means.

In the control unit 62, when the speed change actuator 6 (that is, the motor 50) is started, control is performed so that the rotational power of the motor 1 is temporarily reduced or increased according to the detection result of the slide position detection unit 68. This also serves as the function of the switching control unit 63 configured to do so. Here, the rotational power of the motor 1 is reduced or increased because the relative rotational speed at the time of engagement is reduced as much as possible between the switching member 7 that is slid and the gear member 5 that is engaged after sliding (preferably Because it is zero).

The control unit 62 (switching control unit 63) automatically shifts when the driving state detection unit 60 detects that the load applied to the motor 1 has reached a predetermined level during work with the electric tool.

Hereinafter, the case where the automatic transmission is changed from the first speed to the second speed and the case where the automatic transmission is changed from the second speed to the third speed will be described as an example.

The automatic shift from the first speed to the second speed is performed when the current value flowing through the motor 1 becomes a predetermined value or more, when the rotational speed of the motor 1 becomes a predetermined value or less, or when the current value and the rotational speed are When the predetermined relationship is satisfied, it is detected that the load applied to the motor 1 has reached a predetermined level.

As shown in FIG. 6B, the switching control unit 63, to which the detection result is input, activates the motor 50 of the speed change actuator 6, and the speed change pins 45 and 46 move from the low speed end to the high speed end side of the

cam grooves

41 and 42, respectively. The shift cam plate 8 is rotationally moved so as to move to. The speed change pin 45 inserted into the input side cam groove 41 of the speed change cam plate 8 is slidably driven to the output side according to the cam groove 41 while being guided by the guide groove 48 provided in the gear case 9. The transmission pin 45 slides the ring gear 12 that is the switching member 7 to the output side.

The ring gear 12 that has been slid is first disengaged from the first stage planetary gear 11 and is in the middle of switching shown in FIG. At this time, the ring gear 12 is rotationally fixed with respect to the gear case 9. On the other hand, the second stage planetary gear 21, which is the gear member 5 to be engaged next, is driven to rotate about the axis with respect to the gear case 9 in a form depending on the rotational power of the motor 1.

When the detection result that the ring gear 12 has reached the predetermined switching state shown in FIG. 7 is input from the slide position detection unit 68, the control unit 62 temporarily reduces the rotational power of the motor 1 at that time. (Including zero (stop)). As a result, when the ring gear 12 is engaged with the second stage planetary gear 21 as shown in FIG. 8, the relative rotational speed between the two gears 12 and 21 is reduced (preferably zero), and the impact during engagement is reduced. Suppress. Therefore, automatic shift from the first speed to the second speed is realized smoothly and stably, and gear wear and damage due to a collision are also suppressed.

The automatic shift from 2nd gear to 3rd gear is controlled as follows. That is, when the motor 1 is rotationally driven in the second speed state shown in FIG. 8, when the driving state detection unit 60 detects that the load applied to the motor 1 has reached a predetermined level, the third speed is set. Automatic shift. Specifically, when the current value flowing through the motor 1 becomes a predetermined value or more, when the rotation speed of the motor 1 becomes a predetermined value or less, or this current value and the rotation speed satisfy a predetermined relationship. Is detected, the load applied to the motor 1 has reached a predetermined level.

The control unit 62 to which the detection result is input starts the motor 50 of the speed change actuator 6 and rotates the speed change cam plate 8. The speed change pin 46 inserted through the cam groove 42 on the output side of the speed change cam plate 8 is slid to the output side while being guided by a guide groove 49 provided in the gear case 9. The transmission pin 46 slides the ring gear 32, which is another switching member 7, to the output side.

The ring gear 32 that has been slid is first disengaged from the carrier 24 at the second stage, and reaches a state during switching as shown in FIG. At this time, the ring gear 32 is engaged with the third planetary gear 31 and is not rotationally fixed to the gear case 9.

The ring gear 32 in the midway of switching in FIG. 9 continues to rotate with the rotational inertia when engaged with the carrier 24 at the second speed, but at the same time, the third stage planet driven by the motor 1. The reaction force from the gear 31 receives a rotational force in the direction opposite to the rotational inertia. On the other hand, the engaging tooth portion 40 which is the gear member 5 to which the ring gear 32 is engaged next is fixed to the gear case 9.

The control unit 62 actively utilizes the rotational force in the direction opposite to the rotational inertia to reduce the relative rotational speed between the ring gear 32 and the engaging tooth portion 40 (preferably zero). Yes. That is, when the slide position detecting unit 61 detects that the ring gear 32 has reached the predetermined switching state in FIG. 9, the control unit 62 temporarily stops the sliding movement of the ring gear 32. And the rotational power of the motor 1 is increased temporarily, and the rotational speed with respect to the gear case 9 of the ring gear 32 is reduced rapidly. After that, the sliding movement of the ring gear 32 is resumed, and when the engagement with the engagement tooth portion 40 is performed, the rotation speed of the ring gear 32 is adjusted to be as close to zero as possible.

As a result, as shown in FIG. 10, the impact when the ring gear 32 engages with the engaging tooth portion 40 is suppressed, and a smooth and stable automatic transmission is realized, and the wear and damage of the gear due to the collision are also suppressed. be able to.

Note that the rotational speed may be adjusted by temporarily increasing the rotational power of the motor 1 without temporarily stopping the sliding movement of the ring gear 32. Further, the rotational speed may be adjusted only by temporarily stopping the ring gear 32. Further, as the control for gradually reducing the rotational power of the motor 1 in synchronization with the activation of the speed change actuator 6 and reducing the rotation due to the rotational inertia of the ring gear 32 when engaged with the carrier 24 at the second speed. Also good.

In the case of automatic transmission from the 3rd speed to the 2nd speed, or in the case of the automatic transmission from the 2nd speed to the 1st speed, the control unit 62 is in a state where the rotational power of the motor 1 is stopped or in the middle of switching. The rotational power is reduced or stopped to reduce the relative rotational speed of the switching member 7 and the gear member 5. As a result, smooth and stable automatic gear shifting is realized, and wear and damage of the gear due to a collision are also suppressed.

Further, the control unit 62 (switching control unit 63) may be a control that reduces the rotational power of the motor 1 to some extent from the time when the speed change actuator 6 is activated. In this case, for example, the control unit 62 gradually decreases the rotational power of the motor 1 in synchronization with the activation of the speed change actuator 6, and detects that the ring gear 12 has reached the predetermined switching state in FIG. When the result is input, the rotational power of the motor 1 is further reduced.

As described above, the control unit 62 of the present embodiment activates the speed change actuator 6 according to the driving state of the motor 1 and corresponds to the detected current position of the switching member 7 (ring gears 12 and 32). In this way, the rotational power of the motor 1 is temporarily reduced or increased. This reduction in rotational power includes a case where the motor 1 is stopped. As a result, smooth and stable automatic gear shifting is realized, and wear and damage of the gear due to a collision are also suppressed. The control unit 62 may gradually decrease or increase the rotational power of the motor 1 in synchronization with the activation of the speed change actuator 6.

Further, the automatic shift from the second speed to the first speed or the third speed to the second speed may be performed when the control unit 62 determines that the work is completed. Specifically, after the load of the motor 1 reaches a predetermined level, the motor 1 is stopped driving when the control unit 62 determines that the load is almost lost and the operation of the trigger switch 103 is released. This is an automatic shift when That is, the automatic shift in this state is a shift that returns from the third speed or the second speed to the first speed in preparation for shifting to the next work upon completion of a predetermined work.

In addition, the control unit 62 of the present embodiment corresponds to the position of the switching member 7 (ring gears 12 and 32) detected by the information detection unit 67 and the slide position detection unit 68 when the reduction ratio is switched (at the time of shifting). In this way, control is performed so as to adjust the drive of the speed change actuator 6. Thereby, the slide of the switching member 7 can be adjusted in response to a decrease in the slide amount or moving speed of the switching member 7 due to a decrease in the supply voltage due to the consumption of the battery pack, etc. Slide to a predetermined target position over time to achieve smooth automatic shifting.

Hereinafter, the control of the speed change actuator 6 will be described in detail.

The controller 62 also functions as an actuator controller 64 configured to control the actuator driver 66 so that the switching member 7 reaches the predetermined target position on time. That is, the moving speed of the switching member 7 may vary due to aged deterioration such as a change in supply voltage from the power supply unit 70, misalignment due to gear wear, and increased clearance between gears. In this case, since the sliding amount of the switching member 7 per time is reduced, the switching member 7 does not slide to the predetermined target position within a predetermined time, and not only the shifting does not work, but the operation becomes an obstacle. This also causes an increase in the time required for switching the reduction ratio (switching time).

On the other hand, the control unit 62 grasps the variation in the moving speed of the switching member 7 based on the detection result input from the information detecting unit 67, causes the actuator driving unit 66 to adjust the sliding movement of the switching member 7, and performs switching. The shortage of the amount of slide per time of the member 7 is eliminated. That is, the control unit 62 adjusts the drive of the shift actuator 6 to the actuator drive unit 66 so that the switching member 7 is positioned at a predetermined target position when the drive of the shift actuator 6 has elapsed for a predetermined time. Let At this time, the predetermined time is a switching time required for automatic shifting, and is substantially the same as the driving time of the shifting actuator 6.

Specifically, the information detection unit 67 detects the value of the supply voltage applied from the power supply unit 70 to the actuator drive unit 66 as input / output information when the speed change actuator 6 is driven, and the detection result Is output to the control unit 62. The control unit 62 controls the actuator driving unit 66 so that the sliding amount per time until the switching member 7 reaches a predetermined target position is kept constant according to the input detection result. That is, the control unit 62 causes the actuator driving unit 66 to change the rotational power of the motor 50 at any time according to the detection result of the information detection unit 67 so that the switching member 7 reaches a predetermined target position when a predetermined time elapses. Then, the shift actuator 6 is driven and adjusted. As a result, the shortage of the slide amount due to the variation in the moving speed of the switching member 7 can be suppressed, and the switching member 7 can reach a predetermined target position at a predetermined time, thereby realizing a smooth and stable automatic shift.

Next, other embodiments of the electric tool of the present invention will be described in order. Detailed description of the same configuration as that of the first embodiment will be omitted, and a characteristic configuration different from that of the first embodiment will be mainly described in detail.

(Embodiment 2)
Also in the electric power tool of the present embodiment, the drive of the speed change actuator 6 is adjusted so that the switching member 7 reaches the predetermined target position on time. Thus, the shortage of the sliding amount of the switching member 7 is solved, and the switching time of the reduction ratio is prevented from increasing from a predetermined time, thereby realizing a smooth and stable automatic shift. However, in the present embodiment, the configuration of the drive adjusting unit 61 and the method of adjusting the supply voltage to the speed change actuator 6 are different from those in the first embodiment.

Specifically, the reduction ratio switching means includes a power adjustment unit 69 as shown in FIG. The power adjustment unit 69 includes a step-up / step-down converter configured to step up / down the power supplied from the power supply unit 70, and a control circuit configured to perform PWM control on the converter. The actuator drive unit 66 is configured to supply power so that the supply voltage to the actuator 6 is adjusted to a constant value. That is, the power adjustment unit 69 is configured to detect a supply voltage from the power supply unit 70 to the transmission actuator 6 and drive the transmission actuator 6 according to the detection result of the information detection unit 67. And a drive adjustment unit 61 configured to adjust.

In order to adjust the supply voltage to the shift actuator 6 to a constant value, the power adjustment unit 69 causes the step-up / down converter to supply the actuator drive unit 66 through PWM control of the control circuit in accordance with the supply voltage from the power supply unit 70. Configured to increase or decrease the supply voltage. For example, if the voltage to the speed change actuator 6 is smaller than a predetermined voltage, the power adjustment unit 69 boosts the voltage to the speed change actuator 6 to a predetermined voltage through the step-up / down converter. If the voltage to the speed change actuator 6 is larger than the predetermined voltage, the power adjustment unit 69 steps down the voltage to the speed change actuator 6 to the predetermined voltage through the step-up / down converter. Thus, the voltage to the speed change actuator 6 is maintained at a predetermined voltage regardless of the voltage change and the operation state of the speed change actuator 6.

Thereby, at the time of switching the reduction ratio, the actuator driving unit 66 drives the speed change actuator 6 with a constant supply voltage (predetermined voltage), the switching member 7 is slid at a constant speed, and the switching member 7 is moved at a predetermined time. It reaches a predetermined target position and realizes a smooth and stable automatic shift. In addition, you may reduce the structural member of an electric tool using what used the function of the electric power adjustment part 69 for the control part 62 or the actuator drive part 66. FIG.

(Embodiment 3)
Also in the electric power tool of the present embodiment, the drive of the speed change actuator 6 is adjusted so that the switching member 7 reaches the predetermined target position on time. Thus, the shortage of the sliding amount of the switching member 7 is solved, and the switching time of the reduction ratio is prevented from increasing from a predetermined time, thereby realizing a smooth and stable automatic shift. However, in the present embodiment, the method of adjusting the supply voltage to the speed change actuator 6 is different from that in the first embodiment. And the point which adjusts the supply voltage to the actuator 6 for speed change uniformly is the same as that of Embodiment 2. However, the input / output information detected by the information detection unit 67 is different from that of the second embodiment.

Specifically, the information detection unit 67 is configured to detect a voltage value (voltage value V1) before starting the speed change actuator 6 as input / output information. The power adjustment unit 69 is configured to adjust the supply voltage applied to the gear shift actuator 6 to a voltage value V2 determined according to the detection result (V1). That is, as shown in FIG. 12, the power adjustment unit 69 calculates a voltage value V2 for sliding the switching member 7 at a predetermined movement speed S1 from the detected voltage value V1, and drives according to the calculation result. The adjustment unit 61 performs control to adjust the supply voltage. For example, if the voltage to the speed change actuator 6 is smaller than a predetermined voltage (V2), the power adjustment unit 69 increases the voltage to the speed change actuator 6 to the predetermined voltage (V2) through the step-up / down converter. If the voltage to the shift actuator 6 is greater than the predetermined voltage (V2), the power adjustment unit 69 steps down the voltage to the shift actuator 6 to the predetermined voltage (V2) through the step-up / down converter. The predetermined moving speed S1 is a speed that causes the switching member 7 to reach a predetermined target position when a predetermined time has elapsed during automatic shifting.

Thereby, the switching member 7 can be slid at a constant moving speed (S1), the variation in the moving speed of the switching member 7 is eliminated, the switching member 7 reaches a predetermined target position at a predetermined time, and is smooth. In addition, stable automatic transmission is realized. In addition, you may reduce the structural member of an electric tool using what used the function of the electric power adjustment part 69 for the actuator drive part 66. FIG. Further, the function of the drive adjustment unit 61 may be performed by any of the control unit 62, the actuator drive unit 66, and the power adjustment unit 69.

(Embodiment 4)
Also in the electric tool of this embodiment, the drive of the speed change actuator 6 is adjusted so that the switching member 7 reaches the predetermined target position on time. Thus, the shortage of the sliding amount of the switching member 7 is solved, and the switching time of the reduction ratio is prevented from increasing from a predetermined time, thereby realizing a smooth and stable automatic shift. However, in the present embodiment, the method of adjusting the supply voltage to the speed change actuator 6 is different from that in the first embodiment. And the point which adjusts the supply voltage to the actuator 6 for speed change uniformly is the same as that of Embodiment 3. However, the input / output information detected by the information detection unit 61 is different from that of the third embodiment.

Specifically, the information detection unit 67 is configured to detect the maximum value (maximum current value A1) of the drive current when starting the speed change actuator 6 as input / output information. The power adjustment unit 69 is configured to adjust the supply voltage applied to the speed change actuator 6 to the voltage value estimated from the detection result (A1). That is, the power adjustment unit 69 is configured to estimate the stationary current (voltage) of the motor 50 from the detected maximum current value A1, as shown in FIG. In the example of FIG. 13, the stationary voltage V3 is estimated. In one example, the power adjustment unit 69 holds in advance an equation corresponding to the characteristic diagram of the maximum current and the stationary current (voltage) in FIG. 13, and calculates the stationary current (voltage) from the equation and the detection result (A1). To do. Then, as shown in FIG. 14, the power adjustment unit 69 calculates a voltage value V2 for sliding the switching member 7 at a predetermined moving speed S1 based on the estimation result (estimated voltage V3), and the calculation result (V2). Accordingly, the drive adjustment unit 61 adjusts the supply voltage. As a result, the voltage to the speed change actuator 6 is maintained at a predetermined voltage (V2) as in the third embodiment.

Accordingly, the switching member 7 can be slid at a constant moving speed (S1), variation in the moving speed of the switching member 7 is suppressed, the switching member 7 reaches a predetermined target position at a predetermined time, and is smooth. In addition, a stable automatic transmission is realized. It should be noted that the function of the drive adjustment unit 61 may be any of the control unit 62, the actuator drive unit 66, and the power adjustment unit 69.

(Embodiment 5)
Also in the electric power tool of this embodiment, the drive of the speed change actuator 6 is adjusted, and the switching member 7 is provided so as to reach a predetermined target position in a predetermined time. Thus, the shortage of the sliding amount of the switching member 7 is solved, and the switching time of the reduction ratio is prevented from increasing from a predetermined time, thereby realizing a smooth and stable automatic shift. The present embodiment is the same as the first embodiment in that the moving speed is adjusted at any time while the speed change actuator 6 is being driven. However, the method of adjusting the moving speed of the switching member 7 during driving of the speed change actuator 6 is different from that in the first embodiment.

Specifically, the control unit 62 adjusts the supply power (supply voltage) to the speed change actuator 6 according to the detection result of the information detection unit 67 and the detection result of the slide position detection unit 68. 61 is controlled. Here, the detection result of the information detection unit 67 is the voltage value (voltage value V1) in FIG. 12 or the maximum current value A1 in FIG. Thereby, the dispersion | variation in the moving speed of the switching member 7 can be suppressed, and a smooth and stable automatic transmission is implement | achieved.

Further, when the target position is reached sooner than a predetermined time due to aged deterioration of the gear such as a change in clearance or gear shaft misalignment, the gears (the switching member 7 and the target gear member 5) collide with each other. Wear and damage may occur. On the other hand, in the present embodiment, the switching time is prevented from being reduced from a predetermined time in accordance with the detection result of the slide position detection unit 68 and the detection result of the information detection unit 67, and the gear Suppresses gear wear and damage caused by collisions. It should be noted that the function of the drive adjustment unit 61 may be any of the control unit 62, the actuator drive unit 66, and the power adjustment unit 69.

(Embodiment 6)
Also in the electric tool of the present embodiment, the drive of the shift actuator 6 is adjusted according to the detection results of both the information detection unit 67 and the slide position detection unit 68, and the switching member 7 is reached at a predetermined target position for a predetermined time. It is provided as follows. As a result, smooth and stable automatic gear shifting is realized, and gear wear and breakage due to a collision between gears is also suppressed. However, in the present embodiment, the detection result of the information detection unit 67 used for adjusting the moving speed is different from that of the fifth embodiment.

Specifically, the information detection unit 67 detects the current value A2 and the drive time when the shift actuator 6 is driven as input / output information. As shown in FIG. 15, the control unit 62 calculates the load torque T 1 of the speed change actuator 6 from the current value A 2 detected by the information detection unit 67. In one example, the control unit 62 holds in advance an equation corresponding to the current and load torque characteristic diagram of FIG. 15, and calculates the load torque T1 from the equation and the current value A2. Further, the control unit 62 obtains the rotation speed of the motor 50 at the time of detecting the current value A2 as an index of the moving speed of the switching member 7 from the calculated load torque T1. In this case, the information detection unit 67 may detect the driving time, and the control unit 62 may obtain the rotation speed of the motor 50 from the load torque T1 and the driving time. In one example, the control unit 62 holds in advance a formula corresponding to the characteristic diagram of the load torque and speed (rotation speed) in FIG. 16, and calculates the rotation speed R1 of the motor 50 from the formula and the load torque. The control unit 62 supplies the switching member 7 to the drive adjustment unit 61 so as to reach the target position from the position detected by the slide position detection unit 68 from the position detected by the slide position detection unit 68 based on the obtained moving speed index (rotation speed). Adjust the power. That is, the control unit 62 obtains an index of the moving speed of the switching member 7 when the input / output information is detected based on the load torque T1 and the driving time of the speed change actuator 6, and the obtained moving speed index and the slide position detecting unit 68. In accordance with this detection result, the drive of the shift actuator 6 is adjusted so that the moving speed of the switching member 7 becomes a predetermined speed. The predetermined moving speed S2 is a moving speed that causes the switching member 7 to reach a predetermined target position from the position of the switching member 7 detected by the slide position detection unit 68 when the speed change actuator 6 is driven for a predetermined time. It has become.

As a result, the switching member 7 reaches a predetermined target position at a predetermined time, eliminates the shortage of the sliding amount of the switching member 7, realizes a smooth and stable automatic shift, and reduces the switching time from the predetermined time. This suppresses the wear and breakage of the gear caused by the collision.

It should be noted that the function of the drive adjustment unit 61 may be any of the control unit 62, the actuator drive unit 66, and the power adjustment unit 69. Further, instead of the current value A2, a load sensor T1 of the speed change actuator 6 may be directly detected using a torque sensor or the like, and the detected load torque T1 may be input to the control unit 62 as a detection result.

(Embodiment 7)
Also in the electric tool of the present embodiment, the drive of the shift actuator 6 is adjusted according to the detection results of both the information detection unit 67 and the slide position detection unit 68, and the switching member 7 is reached at a predetermined target position for a predetermined time. It is provided as follows. As a result, smooth and stable automatic gear shifting is realized, and gear wear and breakage due to a collision between gears is also suppressed. However, in the present embodiment, the detection result of the information detection unit 67 used for adjusting the moving speed is different from that of the fifth embodiment.

Specifically, the information detection unit 67 is configured to detect the current value A2 and the voltage value V4 when the shift actuator 6 is driven as input / output information. Further, as shown in FIG. 15, the control unit 62 calculates the load torque T 1 of the speed change actuator 6 from the current value A 2 detected by the information detection unit 67. In one example, the control unit 62 holds in advance an equation corresponding to the current and load torque characteristic diagram of FIG. 15, and calculates the load torque T1 from the equation and the current value A2. Further, as shown in FIG. 16, the control unit 62 uses the calculated load torque T 1 and the voltage value V 4 detected by the information detection unit 67 to move the switching member 7 when the current value A 2 is detected. The number of rotations R1) is estimated, and the drive adjustment unit 61 adjusts the supply power according to the estimation result. In one example, the control unit 62 holds, in advance, an expression corresponding to the characteristic diagram of the load torque and speed (rotation speed) in FIG. 16 for each voltage value V4 to be detected by the information detection unit 67. The rotational speed R1 of the motor 50 is calculated from the expression corresponding to the detected voltage value V4 and the load torque. Based on the movement speed index obtained from the load torque T1 of the speed change actuator 6 and the detection result of the slide position detection section 68, the control section 62 sets the movement speed of the switching member 7 to a predetermined movement speed S2. The drive adjustment unit 61 adjusts the supply voltage. The predetermined moving speed S2 is a moving speed that causes the switching member 7 to reach a predetermined target position from the position of the switching member 7 detected by the slide position detection unit 68 when the speed change actuator 6 is driven for a predetermined time. It has become.

It should be noted that the function of the drive adjustment unit 61 may be any of the control unit 62, the actuator drive unit 66, and the power adjustment unit 69. In addition, the movement speed is not limited to the index of movement, and the movement speed at the time of detecting the current value A2 is obtained, and the drive of the shift actuator 6 is adjusted according to the obtained movement speed and the detection result of the slide position detection unit 68. It may be a thing. Further, instead of the current value A2, a load sensor T1 of the speed change actuator 6 may be directly detected using a torque sensor or the like, and the detected load torque T1 may be input to the control unit 62 as a detection result.

(Embodiment 8)
Also in the electric tool of the present embodiment, the drive of the shift actuator 6 is adjusted according to the detection results of both the information detection unit 67 and the slide position detection unit 68, and the switching member 7 is reached at a predetermined target position for a predetermined time. It is provided as follows. As a result, smooth and stable automatic gear shifting is realized, and gear wear and breakage due to a collision between gears is also suppressed. However, in the present embodiment, the detection result of the information detection unit 67 used for adjusting the moving speed is different from that in the seventh embodiment.

Specifically, the information detection unit 67 is configured to detect the current value A2 and the operation speed S3 when the shift actuator 6 is driven as input / output information. Further, as described above, the control unit 62 calculates the load torque T1 of the speed change actuator 6 from the current value A2 detected by the information detection unit 67 as shown in FIG. Further, as shown in FIG. 17, the control unit 62 estimates the voltage value V5 at the time of detection from the calculated load torque T1 and the operation speed S3 of the speed change actuator 6 detected by the information detection unit 67. Based on the estimated voltage value V5, the control unit 62 causes the drive adjustment unit 61 to adjust the supply voltage so that the moving speed S2 causes the switching member 7 to reach the target position for a predetermined time. That is, the control unit 62 determines the switching member 7 based on the voltage value V5 applied to the transmission actuator 6 obtained from the load torque T1 and the operation speed S3 of the transmission actuator 6 and the detection result of the slide position detection unit 68. The supply voltage is adjusted so that the moving speed becomes a predetermined moving speed S2. The predetermined moving speed S2 is a moving speed that causes the switching member 7 to reach a predetermined target position from the position of the switching member 7 detected by the slide position detection unit 68 when the speed change actuator 6 is driven for a predetermined time. It has become.

It should be noted that the function of the drive adjustment unit 61 may be any of the control unit 62, the actuator drive unit 66, and the power adjustment unit 69. In addition to determining the moving speed S3, an index of the moving speed at the time of detecting the current value A2 is determined, and the shift actuator 6 is driven according to the calculated moving speed index and the detection result of the slide position detecting unit 68. You may adjust. Further, instead of the current value A2, a load sensor T1 of the speed change actuator 6 may be directly detected using a torque sensor or the like, and the detected load torque T1 may be input to the control unit 62 as a detection result.

(Embodiment 9)
Also in the electric power tool of this embodiment, the control unit 62 is provided so that the drive adjusting unit 61 adjusts the drive of the speed change actuator 6. However, in the present embodiment, the moving speed of the switching member 7 is different from that of the first embodiment.

Specifically, the control unit 62 changes the moving speed of the switching member 7 between the control for switching from the first speed to the third speed via the second speed and the control for switching from the third speed to the first speed via the second speed. To control. That is, the control unit 62 increases the moving speed of the switching member 7 when switching from the third speed to the first speed compared to the moving speed of the switching member 7 when switching from the first speed to the third speed, and slides the switching member 7. The switching time differs depending on the direction.

As a result, when it is difficult to request a large output torque at the end of the work, such as a reduction ratio reset operation for returning from the 3rd speed or the 2nd speed to the 1st speed after completion of the work, or a screw loosening operation, the 1st speed to the 2nd speed or 3rd speed Compared with the case of switching to high speed, the switching time of automatic shift is shortened, and the working efficiency is increased.

It should be noted that the function of the drive adjustment unit 61 may be any of the control unit 62, the actuator drive unit 66, and the power adjustment unit 69. Further, the moving speed may be different between the first speed and the second speed, the second speed and the third speed, or may be different for each reduction ratio switching operation. Further, the control unit 62 may change the moving speed of the switching member 7 at the time of the automatic shift according to the presence or absence of the operation load of the motor 1.

Up to this point, the detailed configuration of the power tools of Embodiments 1 to 9 has been described.

As described above, in the power tools of Embodiments 1 to 9, the reduction ratio switching means is configured to adjust the drive of the speed change actuator 6 and the speed change actuator 6 for sliding the switch member 7. The adjustment unit 61 includes a switching control unit 63 configured to change the rotational power of the motor 1, and an actuator control unit 64 configured to control the speed change actuator 6. The actuator control unit 64 controls the drive adjustment unit 61 so as to keep the amount of sliding of the switching member 7 by the speed change actuator 6 per time constant.

In the electric tool having the above configuration, when the reduction ratio is switched, the switching member 7 can be controlled to be positioned at a predetermined target position at a predetermined time, so that the automatic reduction ratio change can be performed smoothly and It can be completed stably at a predetermined time.

In the power tools of Embodiments 1 to 9, the reduction ratio switching means further includes an information detection unit 67 configured to detect input / output information of the speed change actuator 6, and the actuator control unit 64 includes: The drive adjustment unit 61 is controlled according to the detection result of the information detection unit 67. In other words, it becomes possible to control the amount of slide per time of the switching member 7 in accordance with the input / output information of the speed change actuator 6, and the automatic reduction ratio change is completed more smoothly and stably. be able to.

In the electric power tool of the first embodiment, the information detection unit 67 detects the supply voltage applied to the actuator drive unit 66 at any time while the shift actuator 6 is being driven, and the drive adjustment unit 61 uses the change gear at any time according to the detection result. The drive of the actuator 6 is adjusted. As a result, the moving speed of the switching member 7 is adjusted in response to a decrease in the supply voltage accompanying the work of the power tool such as wear of the power supply unit 70, and the switching is performed when the shifting actuator 6 is driven for a predetermined time. The member 7 can reach a predetermined target position.

Furthermore, in the power tools of Embodiments 2 to 8, the drive adjustment unit 61 adjusts the power supplied to the speed change actuator 6 according to the detection result of the information detection unit 67. As a result, the variation in the voltage value of the supplied power due to the aging deterioration of the power supply unit 70 is eliminated, and when the speed change actuator 6 is driven for a predetermined time, the switching member 7 is positioned at a predetermined target position, and smooth In addition, stable automatic transmission can be completed.

In the electric tools of the second and third embodiments, the actuator control unit 64 causes the drive adjustment unit 61 to keep the supply voltage to the speed change actuator 6 constant so that the moving speed of the switching member 7 is kept constant. It is intended to control. As a result, the speed change actuator 6 can be driven with a constant supply voltage, and the speed reduction ratio can be changed more smoothly and stably. Control can be easily performed.

In the power tool of the fourth embodiment, the information detection unit 67 detects the current value flowing through the speed change actuator 6 when the speed change actuator 6 is driven as input / output information. The drive adjustment unit 61 adjusts the power supplied to the speed change actuator 6 according to the detection result of the information detection unit 67. Thereby, the supply voltage applied to the speed change actuator 6 can be adjusted to be constant, and the amount of slide per time when the predetermined target position is reached can be made constant.

In the electric tools of Embodiments 5 to 8, the reduction ratio switching means further includes a slide position detection unit 68 configured to detect the slide position of the switching member 7. The actuator control unit 64 adjusts the power supplied to the speed change actuator 6 according to the detection result of the slide position detection unit 68 and the detection result of the information detection unit 67. As a result, it is possible to control to adjust the moving speed according to the position of the switching member 7, reduce the collision between the switching member 7 and the gear member 5 when the moving speed becomes too fast, and wear or break the gear. Can be suppressed.

Further, in the power tools of the sixth to eighth embodiments, the information detection unit 67 detects input / output information that serves as an index of the load torque of the shift actuator 6, and the control unit 62 uses the detection result as a basis. The drive of the shift actuator 6 is adjusted. As a result, it is possible to control the sliding amount per hour of the speed change actuator 6 according to the load torque, and a smoother and more stable automatic speed change can be completed.

In the power tool of the ninth embodiment, the actuator control unit 64 controls the amount of sliding per time to be different for each sliding direction of the switching member 7. As a result, the switching time is shortened when the change of the output torque at the shift is not so important, or when the speed reduction ratio of the work in the next process is quickly handled (when returning to the first speed), the work efficiency is high. Become.

The present invention has been described above based on the embodiments shown in the accompanying drawings. However, the present invention is not limited to each embodiment, and within the intended scope of the present invention, an appropriate design can be used in each embodiment. It is possible to apply changes and to combine the configurations of the embodiments as appropriate.

In addition, as long as the reduction ratio is switched using the speed change actuator 6, it is not limited to the automatic speed change type electric tool that activates the speed change actuator 6 according to the detection result of the drive state detection unit 60 as in the present embodiment. Absent. For example, the control unit 62 may activate the speed change actuator 6 when the control unit 62 receives a reduction ratio switching command or the like by an operator's external operation or the like.

Claims

A motor as a drive source;
A speed reduction mechanism configured to decelerate the rotational power of the motor and transmit the reduced rotational power;
Reduction ratio switching means configured to switch the reduction ratio of the reduction mechanism section;
An electric tool comprising:
The speed reduction mechanism includes a switching member that includes a shaft and is slidable in the axial direction, and a gear that is switched between an engagement state and a non-engagement state with the switching member according to a sliding position of the switching member in the axial direction. A member, and is configured to switch the reduction ratio through the switching member and the gear member,
The reduction ratio switching means includes a speed change actuator configured to slide the switch member in the axial direction, a drive adjustment unit configured to adjust drive of the speed change actuator, and the speed reduction ratio. A switching control unit configured to reduce a relative rotational speed of the switching member and the gear member at the time of switching, and an actuator control unit configured to control the transmission actuator at the time of switching the reduction ratio. Prepared,
The electric power control device, wherein the actuator control unit is configured to control the drive adjustment unit so as to keep a sliding amount of the switching member per time by the shift actuator constant.
The reduction ratio switching unit further includes an information detection unit configured to detect input / output information of the speed change actuator,
The electric tool according to claim 1, wherein the actuator control unit is configured to control the drive adjustment unit according to a detection result of the information detection unit.
2. The actuator control unit according to claim 1, wherein the drive adjustment unit is configured to keep a supply voltage to the shift actuator constant and to keep a moving speed of the switching member constant. Or the electric tool of Claim 2.
The information detection unit is configured to detect, as the input / output information, a voltage applied to the shift actuator before the shift actuator is activated,
The electric power tool according to claim 2, wherein the drive adjustment unit is configured to adjust electric power supplied to the shift actuator according to a detection result of the information detection unit.
The information detection unit is configured to detect a current value flowing through the shift actuator when the shift actuator is driven as the input / output information.
The electric power tool according to claim 2, wherein the drive adjustment unit is configured to adjust electric power supplied to the shift actuator according to a detection result of the information detection unit.
The reduction ratio switching means further includes a slide position detector configured to detect the slide position of the switching member,
The actuator control unit is configured to adjust power supplied to the gearshift actuator according to a detection result of the slide position detection unit and a detection result of the information detection unit. The electric tool as described in.
The electric power tool according to claim 6, wherein the information detection unit is configured to detect a drive time and a current value of the shift actuator as the input / output information.
The electric power tool according to claim 6, wherein the information detection unit is configured to detect a voltage value and a current value of the shift actuator as the input / output information.
The electric power tool according to claim 6, wherein the information detection unit is configured to detect an operation speed and a current value of the shift actuator as the input / output information.
The electric actuator according to any one of claims 1 to 9, wherein the actuator control unit is configured to control the sliding amount per time to be different for each sliding direction of the switching member. tool.