JP2013039628A - Motor-driven tool - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a motor-driven tool capable of fulfilling various work requests by a simple constitution.SOLUTION: The motor-driven tool is constituted so that a tip tool 119 is driven by a motor 111 to perform a prescribed machining operation on a material to be machined. The motor 111 has: an inner rotor 121; an outer rotor 123; a first stator 125A including an inner rotor driving coil 125a for driving the inner rotor 121; and a second stator 125B including an outer rotor driving coil 125b for driving the outer rotor 123. The motor is constituted so as to be a dual rotor motor in which the inner rotor 121 and the outer rotor 123 are disposed coaxially with each other.

Description

  The present invention relates to an electric tool that drives a tip tool by a motor and thereby performs a predetermined machining operation on a workpiece.

  Japanese Patent Laying-Open No. 2007-295773 (Patent Document 1) discloses a hand-held power tool capable of controlling the output torque of a tip tool driven by a motor. The electric power tool described in the publication is configured to tighten a screw by adding rotation and a circumferential impact to a screw bit as a tip tool.

  However, in the case of a conventional screw tightening machine, if an attempt is made to apply rotation and impact to the tip tool, a complicated apparatus configuration is inevitably unavoidable.

JP 2007-295773 A

  The present invention has been made in view of the above, and an object thereof is to provide an electric tool that can achieve various work requests with a simple device configuration.

  In order to achieve the above object, according to a preferred embodiment of the present invention, an electric tool is configured in which a tip tool is driven by a motor and thereby a predetermined processing operation is performed on a workpiece. The “predetermined machining operation” in the present invention corresponds to a tightening operation of a screw bit or a bolt by a rotational drive of a screw bit or a socket as a tip tool, but is not limited to the tightening operation. It includes a wide range of cutting and drilling operations by rotating around the long axis, and cutting operations by rotating the saw blade.

  In a preferred mode of the electric power tool according to the present invention, as a characteristic configuration, the motor includes an inner rotor, an outer rotor, a first stator including an inner rotor driving coil that drives the inner rotor, and an outer rotor driving coil that drives the outer rotor. A dual stator motor having an inner rotor and an outer rotor arranged coaxially with each other.

  The inner rotor and outer rotor of the dual rotor motor can be driven and stopped individually. For this reason, it is possible to configure the tip tool to be driven using both the inner rotor and the outer rotor, and the tip tool is driven using one of the inner rotor and the outer rotor, and the operation other than the tip tool is performed using the other. It can also be configured to drive the member.

  In the case where the tip tool is driven using both the inner rotor and the outer rotor, for example, when the electric tool is a screw tightener, the screw bit as the tip tool is rotationally driven using one rotor. On the other hand, it is possible to add a circumferential impact to the screw bit using the other rotor. Further, in the case where the tip tool is driven using one of the inner rotor and the outer rotor and the working member other than the tip tool is driven using the other, for example, a motor cooling fan as the working member other than the tip tool. Can be configured to be driven. Thus, according to the present invention, various work requests can be realized with a simple device configuration. In addition, the dual rotor motor can be arranged coaxially with the output shaft that drives the tip tool. With this arrangement, for example, two motors are arranged in series or in parallel. Compared to the above, it is not necessary to project the body of the electric tool to the outside, and a compact electric tool is provided.

According to the further form of the electric tool which concerns on this invention, while having a housing which accommodates a dual rotor motor, an inner motor is comprised by the inner rotor and the 1st stator, and the outer motor is comprised by the outer rotor and the 2nd stator. . The inner motor and the outer motor are arranged in the housing while being shifted in the long axis direction, and a space is formed between the outer peripheral area of the inner motor and the housing. In the present invention, the “long axis direction” refers to the axial direction of the rotation shafts of the inner rotor and the outer rotor.
According to this embodiment, the outer peripheral area of the inner motor can be held (fixed) from the outside by the housing. For this reason, it can hold | maintain firmly with a simple structure compared with the case where the end surface (side surface) of a major axis direction is hold | maintained. The form of holding the outer peripheral area of the inner motor is specifically achieved by fixing the outer peripheral area of the first stator to the housing via a holding member such as an annular member or the like.

According to the further form of the electric power tool according to the present invention, the first stator and the second stator overlap with each other in a state in which the first stator and the second stator are in contact with each other in the radial direction intersecting the major axis direction, and are coupled to each other in the overlapping region. Has been.
According to this embodiment, the first stator and the second stator can be rationally coupled, and specifically, through mechanical coupling using pins, screws, or the like, or through a resin layer formed by resin molding. Bonding with an adhesive or the like is possible.

According to the further form of the electric tool which concerns on this invention, the outer motor is comprised as an axial gap motor arrange | positioned so that an outer rotor and a 2nd stator may mutually oppose in a major axis direction. When configured as an axial gap motor in this way, it is preferable that the first stator and the second stator partially overlap each other in the major axis direction and are coupled in the overlapping region. In the outer motor, it is preferable that the outer peripheral region of the second stator is fixed by a housing via a holding member or directly.
According to this aspect, it is possible to configure a dual rotor motor that uses both a normal radial gap motor and an axial gap motor.

  In the further form of the electric tool which concerns on this invention, it has a deceleration mechanism. The dual rotor motor is configured to drive the tip tool via the speed reduction mechanism. The speed reduction mechanism has at least first and second speed reduction ratios, and switches between the first speed reduction ratio and the second speed reduction ratio by switching at least one of the inner rotor and the outer rotor between a driving state and a stopped state. In this case, the reduction ratio is preferably switched according to any of the current value, torque, rotation speed, and temperature of the dual rotor motor.

In the further form of the electric tool which concerns on this invention, it was set as the structure which changes the output torque output to a front-end tool by switching the 1st and 2nd reduction ratio.
According to this aspect, the output torque of the tip tool can be changed by switching the first and second reduction ratios. For this reason, it is possible to utilize the dual rotor motor in such a manner that the tip tool is driven at a high torque or a low torque according to the load acting on the tip tool at the time of machining operation by the tip tool.

In the further form of the electric tool which concerns on this invention, it was set as the structure which switches the 1st and 2nd reduction ratio and changes the rotational speed of a front-end tool.
According to this aspect, the rotational speed of the tip tool can be changed between a high speed and a low speed by switching the first and second reduction ratios. For this reason, during machining operations with the tip tool, the dual tool is driven in such a way that the tip tool is driven at a high speed when the load is low and the tip tool is driven at a low speed when the load acting on the tip tool is high. The rotor motor can be used.

In the further form of the electric tool which concerns on this invention, it was set as the structure which changes the output torque of a tip tool intermittently by driving the other intermittently in the state which driven one of the inner rotor and the outer rotor continuously.
According to this aspect, the output torque of the tip tool can be intermittently changed. For this reason, if the power tool is, for example, a screw tightener, the output torque is intermittently changed after the screw is seated on the workpiece, so that the output tool rotates in the rotational direction with respect to the screw bit as the tip tool. An impact-type screw tightening machine is constructed without using a mechanical mechanism such as a rotary striking mechanism that applies a striking force intermittently.

According to the further form of the electric tool which concerns on this invention, the reduction gear mechanism is comprised by the planetary gear mechanism. The planetary gear mechanism has a planetary gear that revolves around the sun gear in mesh engagement with both the sun gear and the internal gear, which are arranged coaxially with each other, and both the sun gear and the internal gear. The internal gear is connected to the outer rotor, and the sun gear is connected to the inner rotor. The rotational drive of the outer rotor and the inner rotor is controlled to control the relative rotational difference between the sun gear and the internal gear. The reduction gear ratio is changed by changing the speed.
According to this aspect, it is possible to construct a connection relationship with a reasonable arrangement between the dual rotor motor and the planetary gear mechanism.

In a further form of the electric power tool according to the present invention, the inner rotor is driven at all times when the speed reduction mechanism is constituted by a planetary gear mechanism.
According to this aspect, when the sun gear in the planetary gear mechanism is constantly driven by the inner rotor, the planetary gear engaged with and engaged with the sun gear revolves while rotating. In this case, if the outer rotor is in the stopped state, the internal gear is maintained in the stopped state, but if the outer rotor is driven to rotate in the same direction or in the opposite direction as the inner rotor, the internal gear is moved in the same direction or in the opposite direction as the sun gear. It is driven to rotate, thereby changing the revolution speed of the planetary gear. That is, according to this embodiment, the reduction ratio of the planetary gear mechanism can be changed by switching the outer rotor between the driving state and the stopped state.

In the further form of the electric tool which concerns on this invention, when a reduction mechanism is comprised with a planetary gear mechanism, it is set as the structure by which an outer rotor is always driven. According to the above configuration, when the internal gear in the planetary gear mechanism is constantly driven by the outer rotor, the planetary gear engaged with and engaged with the internal gear revolves while rotating.
According to this aspect, if the inner rotor is in the stopped state, the sun gear is maintained in the stopped state. However, when the inner rotor is driven to rotate in the same direction or in the opposite direction as the outer rotor, the sun gear is moved in the same direction as the internal gear or It is driven to rotate in the reverse direction, which changes the revolution speed of the planetary gear. That is, according to this embodiment, the reduction ratio of the planetary gear mechanism can be changed by switching the inner rotor between the driving state and the stopped state.

According to the further form of the electric power tool according to the present invention, it is interposed between the outer rotor and the internal gear, or between the inner rotor and the sun gear, and transmits torque from the outer rotor and the internal gear side to the tip tool side. In the opposite direction, a clutch that does not transmit torque is provided. And a clutch is set as the structure which locks rotation of an internal gear or a sun gear irrespective of rotation of an outer rotor or an inner rotor according to the torque which acts on a front-end tool.
According to this aspect, when the outer rotor or the inner rotor is put in a stopped state, the rotation of the internal gear or the sun gear can be locked by the clutch, thereby reversing the power from the internal gear or the sun gear to the outer rotor or the inner rotor. The motor can be protected by shutting off the input.

According to the further form of the electric tool which concerns on this invention, it has a fan as an operation member other than a tip tool. One of the inner rotor and the outer rotor in the dual rotor motor is configured to drive the tip tool, and the other is configured to drive the fan.
According to this aspect, the fan provided as an operation member other than the tip tool can be driven coaxially.

  According to the further form of this invention, an outer rotor has the extension area | region where the one end part of the major axis direction was extended longer than the one end part of the second stator and the inner rotor in the major axis direction. And the fan is arrange | positioned inside the extension area | region of the said outer rotor. With such a configuration, a rational arrangement configuration can be constructed. In this case, the fan can be configured to be driven constantly or intermittently.

  According to the further form of the electric tool which concerns on this invention, a fan is comprised as a cooling fan which cools a dual rotor motor. The cooling fan is configured to be driven at all times or configured to be driven intermittently according to at least one of the temperature, the rotational speed, the torque, and the current value of the dual rotor motor.

  According to the further form of the electric tool which concerns on this invention, a fan is comprised as a dust suction fan which absorbs the dust which arises in the process operation, and is driven according to a dust suction request | requirement. Note that the “dust-requiring request” here typically means that when the power tool is a drilling tool or a cutting tool, the tip tool is rotationally driven to perform the drilling or cutting operation. Applicable.

  According to the present invention, an electric tool capable of achieving various work requests with a simple device configuration is provided.

It is a sectional side view showing the whole screw driver composition concerning a 1st embodiment of the present invention. It is an expanded sectional view which shows the principal part of the said screw driver. It is sectional drawing of the bidirectional | two-way one-way clutch cut | disconnected by the AA line of FIG. 1, and shows a lock release state. It is sectional drawing of the bidirectional | two-way one-way clutch similarly cut | disconnected by the AA line of FIG. 1, and shows a locked state. It is an external view which shows the stator in a dual rotor motor. FIG. 6 is a sectional view taken along line B-B in FIG. 5. It is the perspective view seen from the left of FIG. It is the perspective view seen from the right side of FIG. It is sectional drawing shown typically for demonstrating the holding | maintenance (fixation) structure of the stator in a dual rotor motor. It is a D arrow line view of FIG. 9, and shows only a motor. FIG. 10 is a C arrow view of FIG. 9 and shows only the motor. It is sectional drawing shown typically for demonstrating the modification regarding the structure of a dual rotor motor. It is a sectional side view which shows the structure of the screw driver which concerns on the 2nd Embodiment of this invention. It is an expanded sectional view which shows the principal part of the said screw driver. It is sectional drawing of the bidirectional | two-way one-way clutch cut | disconnected by the EE line | wire of FIG. 13, and shows a lock release state. It is sectional drawing of the bidirectional | two-way one-way clutch similarly cut | disconnected by the EE line | wire of FIG. 13, and shows a locked state. It is a sectional side view which shows the structure of the screw driver which concerns on the 4th Embodiment of this invention. It is sectional drawing of the cooling fan cut | disconnected by the FF line of FIG. It is a sectional side view which shows the structure of the screw driver which concerns on the 5th Embodiment of this invention.

(First embodiment of the present invention)
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. In the present embodiment, a rechargeable screw driver will be described as an example of a hand-held power tool. As shown in FIG. 1, the screw driver 101 according to the present embodiment generally includes a main body 103 that forms an outline of the screw driver 101, and a hand grip that is integrally connected to the main body 103. Handle) 109 is the main component. A screw bit 119 is detachably attached to the tip of the spindle 115 via a bit holder 117 in the tip region of the main body 103 (on the left side in the figure and opposite to the handgrip 109). The main body 103 constitutes a “tool main body”. The screw bit 119 corresponds to the “tip tool” in the present invention. In this embodiment, for convenience of explanation, the screw bit 119 side is the front side, and the opposite side is the rear side.

  The main body 103 includes a motor housing 105 that houses the drive motor 111, a planetary gear mechanism 113 that serves as a speed reduction mechanism and a spindle 115 that serves as an output shaft disposed in front of the drive motor 111 (left side in FIGS. 1 and 2). And the like, and a gear housing 107 that accommodates the main body. The drive motor 111 corresponds to the “motor” and “dual rotor motor” in the present invention. The hand grip 109 extends downwardly intersecting the long axis direction of the main body 103 (long axis direction of the screw bit 119), and a battery serving as a power source for the drive motor 111 is accommodated in the extended end portion. The attached battery pack 110 is detachably attached.

  FIG. 2 shows the configuration of the main part of the screw driver 101. As illustrated, the drive motor 111 includes an inner rotor 121 (first rotor), an outer rotor 123 (second rotor), and an inner rotor stator around which an inner rotor driving coil 125a for driving the inner rotor 121 is wound. 125A (stator) (hereinafter referred to as an inner stator) and an outer rotor stator (hereinafter referred to as an outer stator) 125B (stator) around which an outer rotor driving coil 125b for driving the outer rotor 123 is wound. An inner rotor 121 is arranged inside the inner stator 125A, and an outer rotor 123 is arranged outside the outer stator 125B as a dual rotor motor arranged coaxially with each other. The inner stator 125A corresponds to the “first stator” in the present invention, and the outer stator 125B corresponds to the “second stator” in the present invention. Further, the “inner rotor drive coil 125a” and the outer rotor drive coil 125b constitute a “drive coil mechanism”.

  As shown in FIGS. 5 to 8, the inner stator 125 </ b> A and the outer stator 125 </ b> B are both formed in a substantially donut shape. The inner stator 125A protrudes in an inner diameter direction from an annular yoke portion 125A1 and a spaced position on the inner circumferential surface of the yoke portion 125A1, and a plurality of inner rotor driving coils (not shown for convenience in FIGS. 5 to 8) are wound around the inner stator 125A. Teeth portion 125A2 and a plurality of slots. The outer stator 125B protrudes in an outer diameter direction from a ring-shaped stator main body portion 125B1 and a spaced position on the outer peripheral surface of the stator main body portion 125B1, and an outer rotor drive coil (not shown for convenience in FIGS. 5 to 8). A plurality of teeth portions 125B2 to be wound and a plurality of slots are provided.

  In the present embodiment, as shown in FIG. 10, an inner rotor 121 having four magnets 121b fixed on the outer peripheral surface and an inner stator 125A having six slots constitute a four-pole six-slot inner motor. The Further, as shown in FIG. 11, an outer rotor 123 having eight magnets 123b fixed to the inner peripheral surface and an outer stator 125B having eight slots constitute an 8-pole 6-slot outer motor. As shown in FIGS. 2 and 9, the inner motor and the outer motor are arranged in the motor housing 105 so as to be shifted in the long axis direction, specifically, the outer motor is located at the front and the inner motor is located at the rear. It is said.

  The yoke portion 125A1 of the inner stator 125A and the yoke portion 125B1 of the outer stator 125B are formed to have substantially the same inner diameter and outer shape, and the yoke portion 125B1 of the outer stator 125B is formed in front of the yoke portion 125A1 of the inner stator 125A. The rear surfaces are joined in a superposed state (see FIGS. 6 and 9). That is, the inner stator 125A and the outer stator 125B are coupled to each other by a plurality of pins 125c (see FIG. 9) as coupling members in which yoke portions 125A1 and 125B1 as overlapping regions are arranged at predetermined intervals in the circumferential direction. Is done. In addition, as a coupling means for the inner stator 125A and the outer stator 125B, in addition to the above-described pin 125c, for example, mechanical coupling using a plurality of screws is possible, a coupling structure through a resin layer by resin molding, or Bonding with an adhesive is possible.

  As shown in FIGS. 2 and 9, when the inner motor and the outer motor are disposed in the motor housing 105, the inner stator 125 </ b> A and the outer stator 125 </ b> B are coupled to each other while being shifted in the long axis direction as described above. Thus, an annular space is formed between the inner wall surface of the motor housing 105 and the outer peripheral region of the yoke portion 125A1 of the inner stator 125A. In the present embodiment, the outer peripheral area of the yoke portion 125A1 is held from the outside by the motor housing 105 via the holding member 126 using this space. The holding member 126 is provided, for example, as an annular member formed as a separate member from the motor housing 105 or as an annular member integrally formed so as to project inwardly on the inner wall of the motor housing 105, and the outer peripheral side is provided on the motor housing. The inner peripheral side is fixed to the yoke portion 125A1 of the inner stator 125A.

  The inner rotor 121 is disposed inside the inner stator 125A. The inner rotor 121 is rotatably supported by a bearing housing portion 127A disposed on the inner periphery of the outer stator 125B on the front side via a bearing 127, and is rotatably supported on the motor housing 105 via a bearing 128 on the rear side. Has been. The outer rotor 123 is formed in a substantially cylindrical shape, and is disposed outside the outer stator 125B. The outer periphery of the outer rotor 123 is rotatably supported by the motor housing 105 via front and rear bearings 129. The inner rotor 121 and the outer rotor 123 are configured to be independently driven and stopped. A predetermined air gap is formed between the inner rotor 121 and the inner stator 125A and between the outer rotor 123 and the outer stator 125B.

  As shown in FIG. 2, a planetary gear mechanism 113 is disposed in front of the drive motor 111 configured as described above, and the rotational output of the drive motor 111 is decelerated by the planetary gear mechanism 113 and is rotated by the spindle 115. Is transmitted to the screw bit 119 held on the spindle 115 via the bit holder 117. The planetary gear mechanism corresponds to the “deceleration mechanism” in the present invention.

  The planetary gear mechanism 113 includes a first sun gear 131, a first internal gear (ring gear) 133, a plurality of first planetary gears 135, a first carrier 137, a second sun gear 139, a second internal gear 141, and a plurality of first gears. The second planetary gear 143 and the second carrier 145 are configured to reduce the rotational output of the inner rotor shaft 121a and transmit it to the spindle 115.

  The first sun gear 131 is coupled to the inner rotor shaft 121a of the inner rotor 121 and rotates integrally. The first internal gear (ring gear) 133 is a ring-shaped member whose outer surface is rotatably supported by the gear housing 107 and teeth are formed on the inner side, and the outer rotor 123 passes through a bidirectional one-way clutch 151 described later. Driven by rotation. The plurality of first planetary gears 135 mesh with and engage with both the first sun gear 131 and the first internal gear 133 and revolve (revolve) around the rotation axis of the first sun gear 131. The first carrier 137 rotatably supports the plurality of first planetary gears 135 and rotates coaxially with the first sun gear 131. The second sun gear 139 is integrally formed on the outer circumferential surface on the one end (front end) side of the first carrier 137 in the long axis direction. The second internal gear 141 is fixed to the gear housing 107 and is always kept stopped. The plurality of second planetary gears 143 mesh with and engage with both the second sun gear 139 and the second internal gear 141 and revolve (revolve) around the rotation axis of the second sun gear 139. The second carrier 145 rotatably supports the second planetary gear 143 and is connected to the spindle 115 via the overload clutch 147.

  The overload clutch 147 is a known mechanical element that is provided to cut off the transmission of the rotational force from the second carrier 145 to the spindle 115 when an excessive load is applied to the spindle 115. Is omitted. In the planetary gear mechanism 113 in the present embodiment, the first first carrier 137 that supports the first planetary gear 135 and the second carrier 145 that supports the second planetary gear 143 are connected in two stages in the major axis direction. However, it is not always necessary to have two stages.

  The outer rotor 123 is connected to the first internal gear 133 of the planetary gear mechanism 113 via the bidirectional one-way clutch 151. The bidirectional one-way clutch 151 corresponds to the “clutch” in the present invention. As shown in FIGS. 3 and 4, the bidirectional one-way clutch 151 forms an outer shape of the bidirectional one-way clutch 151, a ring-shaped fixed outer ring portion 158 formed integrally with the gear housing 107, and an input shaft. A power transmission unit 153 formed integrally with the outer rotor 123, a power receiving member 157 joined to the first internal gear 133, and disposed between the power transmission unit 153 and the power receiving member 157, and on the output side. When a rotational force is input from a certain first internal gear 133 to the outer rotor 123 on the input side, the cylindrical lock pin 159 that locks the rotation of the first internal gear 133 is mainly configured.

  The power transmission unit 153 has a plurality of cross sections (four in the case of the present embodiment, at intervals of 90 degrees) extending at a predetermined interval in the long axis direction at a predetermined interval in the front region of the outer rotor 123. It is comprised by the circular-arc-shaped member, and is arrange | positioned inside the fixed outer ring | wheel part 158 so that relative rotation is possible. The power receiving member 157 is formed in a disk shape having a circular hole through which the first sun gear 131 can pass in a loose fit, and is disposed inside the power transmission unit 153 so as to be relatively rotatable. The power receiving member 157 has two power receiving portions 155 that protrude in the outer diameter direction with a phase difference of 180 degrees on the outer surface, and the power receiving portion 155 is in the space between the adjacent power transmitting portions 153. The two spaces having a phase difference of 180 degrees are arranged with a predetermined gap in the circumferential direction. The lock pin 159 is disposed in the other two spaces having a phase difference of 180 degrees in the space between the adjacent power transmission units 153.

  When the outer rotor 123 is driven to rotate clockwise, the one power transmission portion 153 that faces the power receiving portion 155 of the power receiving member 157 across the power receiving portion 155 contacts the power receiving portion 155 in the circumferential direction, and the first internal When the rotational force is transmitted clockwise to the lug gear 133 and rotated counterclockwise, the other power transmission portion 153 contacts the power reception portion 155 in the circumferential direction with the power reception portion 155 interposed therebetween. The rotational force is transmitted to the first internal gear 133 counterclockwise. A case where the outer rotor 123 is driven to rotate counterclockwise is shown in FIG.

  The lock pin 159 is disposed between the outer surface of the power receiving member 157 and the inner surface of the fixed outer ring portion 158 in the space between the adjacent power transmission portions 153, and the power receiving member 157 in the space where the lock pin 159 is disposed. A tangential plane region 157a is formed on the outer surface. Therefore, as shown in FIG. 3, when the outer rotor 123 is driven to rotate, the lock pin 159 causes the relative rotation difference between the power receiving member 157 and the fixed outer ring portion 158 to change between the outer surface of the power receiving member 157 and the fixed outer ring portion. It enters the wedge-shaped space between the inner surface of 158 and tries to bite it, but is held in the flat region 157a by being pushed by the end surface on the front end side in the rotational direction of the power transmission portion 153. Therefore, the lock pin 159 is not engaged and the rotational force of the outer rotor 123 is transmitted to the first internal gear 133 via the power receiving member 157.

  On the other hand, when a rotational force is input from the output side to the input side, for example, a load is applied to the first internal gear 133 (spindle 115) side, and the power receiving member 157 acts on the power transmission unit 153 in the state shown in FIG. When attempting to rotate relatively, the power receiving member 157 comes into contact with and engages with the inner surface of the fixed outer ring portion 158 via the lock pin 159. That is, the lock pin 159 enters and engages with the wedge-shaped space between the outer surface of the power receiving member 157 and the inner surface of the fixed outer ring portion 158, and thereby the power receiving member 157 is fixed (locked) to the fixed outer ring portion 158.

  In this way, the bidirectional one-way clutch 151 applies the rotational force of the outer rotor 123 on the input side (drive side) to the first internal gear 133 (spindle 115) on the output side (driven side) in both the clockwise and counterclockwise directions. Can be transmitted to the output side, and when the rotational force is going to be reversely input from the output side to the input side due to the load acting on the output side, both the clockwise and counterclockwise directions are locked and output. It is provided as a mechanical element that blocks the rotational force from the side to the input side.

  In the present embodiment, when the inner rotor 121 of the drive motor 111 is energized while the first internal gear 133 is fixed, the spindle 115 rotates at a predetermined reduction ratio predetermined in the planetary gear mechanism 113. Is done. In this state, when the outer rotor 123 is rotated in the same direction as the rotation direction of the inner rotor 121, the first internal gear 133, which is a reaction force receiving member, is rotated in the same direction as the first sun gear 131. Since the rotation speed (revolution speed) of the first planetary gear 135 around the first sun gear 131 increases by the rotation of the first internal gear 133, the rotation speed of the spindle 115 increases. On the other hand, when the outer rotor 123 is rotated in the opposite direction, the revolution number of the first planetary gear 135 is reduced by the rotation amount of the first internal gear 133, so that the rotation speed of the spindle 115 is reduced.

  As described above, according to the present embodiment, the outer rotor 123 is switched between the stopped state and the driving state in the same direction or in the opposite direction as the inner rotor 121 while the inner rotor 121 is continuously driven. Thus, the revolution number of the first planetary gear 135 (the rotation number of the first carrier 137) can be changed, and the reduction ratio of the planetary gear mechanism 113 can be switched. That is, the output torque and rotational speed output to the spindle 115 can be changed by switching the reduction ratio of the planetary gear mechanism 113. Note that switching of the reduction ratio is configured to be performed in accordance with a load acting on the spindle 115, for example, a drive current, torque, rotation speed, temperature, and the like of the drive motor 111. In the state where the inner rotor 121 is always driven, the reduction ratio when the outer rotor 123 is switched to the stopped state and the reduction ratio when the outer rotor 123 is switched to the driving state are the “first and second reduction ratios” in the present invention. ".

  When a screw or bolt (hereinafter referred to as a screw or the like) as a fixture is tightened by the screw driver 101, the screw or the like is pressed against a workpiece as a work object via the screw bit 119. In this state, the trigger 109a disposed on the hand grip 109 is pulled and the drive motor 111 is energized. As a result, the spindle 115 is rotationally driven via the planetary gear mechanism 113, and a screw bit 119 that rotates together with the spindle 115 can perform tightening work such as a screw.

  In this case, in the present embodiment, the first sun gear 131 is always driven by the inner rotor 121 of the drive motor 111, and the first internal gear 133 is variable by the outer rotor 123.

  Specifically, during driving of the screw bit 119 with the inner rotor 121 driven at all times, the outer rotor 123 is driven intermittently, that is, driven and stopped, thereby being driven with the output torque output by the inner rotor 121. Further, the output torque output from the outer rotor 123 is intermittently added (added) to the screw bit 119, whereby the torque for driving the screw bit 119 can be changed intermittently. In the following description, intermittently changing the torque is also referred to as torque ripple.

  As described above, according to the present embodiment, by intermittently driving the outer rotor 123, the output torque output to the screw bit 119 is temporarily increased and then immediately returned to the original state. Can be repeated. As a result, a reaction force required to hold the screw driver 101 can be reduced, and a screw that can be easily held by a person even though a screw tightening operation can be performed with a torque larger than a normal tightening torque. A driver 101 can be provided.

  The generation of torque ripple due to intermittent driving of the outer rotor 123 may be performed over the entire period from the start to the completion of the screw tightening operation in the constant drive by the inner rotor 121 of the screw bit 119 or in part. You may do it. For example, when the screw is seated on the workpiece and the load (tightening torque) is increased during the screw tightening operation by the screw bit 119 driven by the inner rotor 121, the outer rotor 123 is intermittently operated. A mode in which torque ripple is generated by driving in a normal manner is preferable.

  Therefore, according to the present embodiment, without using a mechanical rotary hitting mechanism that intermittently applies a hitting force to the screw bit 119 in the rotation direction, the same impact type as that provided with the rotary hitting mechanism is used. The screw driver 101 can be constructed. When the outer rotor 123 is intermittently driven during the driving of the screw bit 119 by the inner rotor 121, for example, the drive current, torque, rotational speed, and temperature of the inner rotor 121 that is always driven are adjusted. Illustration is omitted for convenience so that intermittent driving of the outer rotor 123 is started when at least one of them is detected by a detector and the detected value detected by the detector reaches a specified value specified in advance. It can be configured to control using a motor control device (controller).

  The first internal gear 133 receives a reaction force when the screw bit 119 is rotationally driven by the inner rotor 121. For this reason, in order to generate a torque ripple by driving the outer rotor 123, it is necessary that the outer rotor 123 generate a larger torque than the inner rotor 121. While torque ripple is not generated, that is, while the screw bit 119 is driven only by driving the inner rotor 121, it is necessary to maintain the first internal gear 133 in a fixed state. If the fixed state of the first internal gear 133 is maintained only by the torque of the outer rotor 123, the outer rotor 123 is used in a locked state, and there is a possibility of motor burning. However, according to the present embodiment, the two-way one-way clutch 151 provided between the outer rotor 123 and the first internal gear 133 of the planetary gear mechanism 113 moves from the driven first internal gear 133 to the input outer rotor 123. Therefore, the first internal gear 133 can be maintained in a fixed state. As a result, the outer rotor 123 can be protected from burning.

  Further, in the present embodiment, the dual rotor motor constituting the drive motor 111 is arranged coaxially with the spindle 115 that drives the screw bit 119, so that, for example, two motors are arranged in parallel. Compared to the case, it is not necessary to project the body outward, and a compact screwdriver 101 is provided.

  In the present embodiment, the inner rotor 121 and the inner stator 125A constitute an inner motor, and the outer rotor 123 and the outer stator 125B constitute an outer rotor. The inner motor and the outer motor are arranged in the motor housing 105 in a state shifted in the long axis direction, whereby the inner motor (specifically, the inner stator 125A) is disposed between the outer peripheral region and the inner wall surface of the motor housing 105. The space is formed. For this reason, the holding member 126 is installed using the space, and the outer peripheral region of the inner stator 125 </ b> A of the inner motor can be held (fixed) by the motor housing 105 via the holding member 126. For this reason, for example, the stator can be firmly held with a simple structure as compared with the configuration in which the end surface (side surface) in the major axis direction of the stator is held.

  Further, in the present embodiment, the inner stator 125A and the outer stator 125B are configured to overlap each other in the state where the yoke portions 125A1 and 125B1 are in contact with each other, and are configured to be coupled to each other by the pin 125c in the overlapping region. Thus, the inner stator 125A and the outer stator 125B can be rationally coupled.

  In the present embodiment, a cooling fan 161 (see FIG. 2) for cooling the motor is provided in the inner rotor 121 that is always driven. The cooling fan 161 is disposed at a long-axis direction end (rear end) of the inner rotor 121 opposite to the first sun gear 131, and is an intake port (illustrated for convenience) formed at the rear end of the motor housing 105. The external air is taken into the inner space of the motor housing and circulated forward in the long axis direction, and the drive motor 111 is cooled by exhausting it from the exhaust port (not shown for convenience) to the outside of the motor housing. be able to.

  Next, a modification of the drive motor 111 according to the first embodiment will be described with reference to FIG. A drive motor 111 according to this modification includes an inner rotor 121 (first rotor), an outer rotor 123 (second rotor), and an inner rotor stator around which an inner rotor driving coil 125a for driving the inner rotor 121 is wound. 125A (stator) (hereinafter referred to as an inner stator) and an outer rotor stator (hereinafter referred to as an outer stator) 125B (stator) around which an outer rotor driving coil 125b for driving the outer rotor 123 is wound. The inner rotor 121 is disposed inside the inner stator 125A, the outer rotor 123 is disposed oppositely on the front surface of the outer stator 125B, and the inner rotor 121 and the outer rotor 123 are configured as a dual rotor motor disposed coaxially with each other. .

  In other words, the dual rotor motor of the modification is configured as a radial motor in which the inner rotor 121 and the inner stator 125A are opposed to each other in the radial direction, while the outer motor 123 and the outer stator 125B. Is different from the first embodiment described above in that it is configured as an axial gap motor in which the outer rotor 123 and the outer stator 125B are arranged so as to face each other in the long axis direction.

  As shown in the figure, the inner motor and the outer motor constituted by the inner rotor 121 and the inner stator 125A are shifted in the long axis direction, specifically, arranged in the front and rear directions so that the outer motor is located at the front and the inner motor is located at the rear. . Then, the outer periphery of the front end portion of the yoke portion 125A1 of the inner stator 125A in the inner motor and the inner periphery of the yoke portion 125B1 of the outer stator 125B in the outer motor are set as regions overlapping each other in the major axis direction, and the yoke portions 125A1 and 125B1 For example, they are bonded to each other through a resin layer formed by resin molding or by an adhesive.

  In the case of the modified example, the outer motor 123 and the outer stator 125B are axial gap motors that face each other in the long axis direction, so that a space is formed between the outer peripheral surface of the outer stator 125B and the inner wall surface of the motor housing 105. Therefore, using this space, for example, the outer stator 125 </ b> B is formed on the outer side with an annular holding portion 105 </ b> A (or an annular member formed separately from the motor housing 105) integrally formed on the inner wall of the motor housing 105. It is set as the structure hold | maintained from. That is, according to the modification, in addition to the configuration in which the outer peripheral region of the inner stator 125A of the inner motor is held by the motor housing 105 from the outside via the holding member 126, the outer peripheral region of the outer stator 125B is held by the motor housing 105 from the outer side. Since the portion 105A is configured to be held from the outside, it is possible to hold the stator more firmly.

  Moreover, according to the modification, the outer stator 125B of the outer motor is disposed outside the inner stator 125A. Therefore, the front surface of the yoke portion 125A1 of the inner stator 125A can be held by a part 127a of the bearing housing 127A that extends toward the yoke portion 125A1 as shown in the drawing. Thereby, the holding of the stator can be further strengthened.

(Second embodiment of the present invention)
Next, a second embodiment will be described with reference to FIGS. In this embodiment, as shown in FIGS. 13 and 14, the first internal gear 133 is always driven by the outer rotor 123, and the first sun gear 131 is made variable by the inner rotor 121. For this purpose, the outer rotor 123 is configured to be directly connected to the first internal gear 133, while the bidirectional one-way clutch 151 is disposed between the inner rotor shaft 121 a of the inner rotor 121 and the first sun gear 131. Except for the above configuration, the configuration including the configuration in which the outer peripheral region of the inner stator 125A is held by the holding member 126 is configured in the same manner as in the first embodiment described above. Accordingly, the same reference numerals are given to the same constituent members.

  As shown in FIGS. 15 and 16, the bidirectional one-way clutch 151 basically has the same configuration and function as the bidirectional one-way clutch 151 described in the first embodiment. However, the fixed outer ring portion 158 constituting the outer shape of the bidirectional one-way clutch 151 is interposed between the inner rotor shaft 121a and the first sun gear 131, and the outer stator 125B is located in front of the inner stator 125A of the drive motor 111. The first sun gear 131 is formed in a substantially cup shape with a circular hole through which the first sun gear 131 penetrates in a loosely fitting manner. Further, the four power transmission portions 153 arranged at predetermined intervals in the circumferential direction are integrally formed with a disk-shaped power transmission member 152 that is joined to the inner rotor shaft 121a and rotates together with the inner rotor shaft 121a. Further, the power receiving member 157 having the power receiving portion 155 is joined to the first sun gear 131 and is configured to rotate together with the first sun gear 131. Other configurations are the same as those of the bidirectional one-way clutch 151 described in the first embodiment.

  Therefore, when the inner rotor 121 is driven, as shown in FIG. 15, the lock pin 159 is pushed by the end surface on the front end side in the rotation direction of the power transmission portion 153, thereby causing the outer surface of the power receiving member 157 and the fixed outer ring portion 158 to move. It does not enter the wedge-shaped space between the inner surfaces. For this reason, the power transmission unit 153 contacts the power receiving unit 155 in the circumferential direction and transmits the rotational force to the first sun gear 131. On the other hand, in the state shown in FIG. 16, when a rotational force is input from the output side to the input side, that is, a load is applied to the first sun gear 131 (spindle 115) side, and the power receiving member 157 is applied to the power transmission member 152. On the other hand, when it is attempted to rotate relatively, the lock pin 159 enters and engages with a wedge-shaped space between the outer surface of the power receiving member 157 and the inner surface of the fixed outer ring portion 158, whereby the power receiving member 157 is fixed to the fixed outer ring portion 158. (Locked).

  That is, when the input-side (drive-side) inner rotor 121 is driven, the bidirectional one-way clutch 151 applies the rotational force of the inner rotor 121 to the output-side (driven-side) first in both clockwise and counterclockwise directions. 1 The sun gear 131 (spindle 115) can be transmitted, and when the load acts on the output side and the rotational force is going to be reversely input from the output side to the input side, the clockwise and counterclockwise directions Both directions are locked and the rotational force from the output side to the input side is cut off.

  In the present embodiment, the first internal gear 133 is always driven by the outer rotor 123 of the drive motor 111, and the first sun gear 131 is variable by the inner rotor 121. Accordingly, during driving of the spindle 115 (screw bit 119) by driving the outer rotor 123, the inner rotor 121 is driven intermittently, that is, by driving and stopping repeatedly, the outer rotor 123 is being driven by the output torque output by the outer rotor 123. Further, the output torque output from the inner rotor 121 is intermittently added to the screw bit 119. That is, according to the present embodiment, the torque for driving the screw bit 119 can be changed intermittently.

  As described above, according to the present embodiment, by intermittently driving the inner rotor 121, the output torque output to the screw bit 119 is temporarily increased and then immediately returned to the original state. Can be repeated. For this reason, during the screw tightening operation, for example, when the screw is seated on the workpiece and the load (tightening torque) increases, the inner rotor 121 is intermittently driven to generate a torque ripple. The screw tightening operation can be performed with a tightening torque larger than the tightening torque.

  In the case of the present embodiment, the first sun gear 131 receives a reaction force when the screw bit 119 is rotationally driven by the outer rotor 123. For this reason, in order to generate torque ripple by intermittent driving of the inner rotor 121, it is necessary for the inner rotor 121 to generate a larger torque than the outer rotor 123. While the torque ripple is not generated, it is necessary to stop the energization drive of the inner rotor 121 and maintain the first sun gear 131 in a fixed state. If the maintenance is performed only with the torque of the inner rotor 121, the motor may be burned out. There is. In the present embodiment, the two-way one-way clutch 151 provided between the inner rotor 121 and the first sun gear 131 blocks reverse input of power from the driven first sun gear 131 to the input inner rotor 121, The first internal gear 133 can be maintained in a fixed state. Thereby, the outer rotor 123 can be protected from burning.

  In the present embodiment, a cooling fan 163 for cooling the motor is provided in the outer rotor 123 that is always driven. The cooling fan 163 is disposed on the inner peripheral surface of the outer end of the outer rotor 123 on the opposite side of the first internal gear 133 in the axial direction (rear end), and is supplied to the outside air from the intake port formed at the rear end of the motor housing 105 Then, the drive motor 111 is cooled by taking it into the space inside the motor housing and circulating it forward in the long axis direction. The outside air that has flowed into the motor housing inner space flows into the motor through gaps such as between the outer stator 125B and the outer rotor 123, between the inner stator 125A and the inner rotor 121, etc., thereby cooling the drive motor 111, and then the outer rotor. It flows out to the outside of the motor through a communication window 123a (see FIG. 14) penetrating in the radial direction formed in the front region of 123, and further, after passing between the motor housing 105 and the gear housing 107, is discharged to the outside from the exhaust port. The In this case, the holding member 126 that holds the inner stator 125 </ b> A is preferably provided with a ventilation hole penetrating in the front-rear direction for guiding the cooling air between the outer stator 125 </ b> B and the outer rotor 123.

  According to the present embodiment, not only the above-described operation and effect but also the same operation and effect as the first embodiment described above are provided, but the description is omitted in order to avoid redundant description.

(Third embodiment of the present invention)
Next, a third embodiment of the present invention will be described with reference to FIGS. In this embodiment, the screw bit 119 is always driven by using one rotor of the drive motor 111, and according to the load (tightening torque) acting on the screw bit 119 (spindle 115) using the other rotor. Thus, the reduction ratio of the planetary gear mechanism 113 is switched so that the rotational speed (screw tightening speed) of the screw bit 119 can be automatically changed.

  The overall configuration of the screw driver 101 is the same as that of the first embodiment described above, and a description thereof will be omitted. In this embodiment, the inner rotor 121 and the outer rotor 123 are driven simultaneously when the trigger 109a is pulled.

  For example, in a state where the load from the start of the screw tightening operation until the screw is seated on the workpiece (the head of the screw contacts the workpiece) is small, the reaction of the rotational driving force received by the first internal gear 133 is reduced. The power is small. In this state, the first sun gear 131 is rotationally driven by the inner rotor 121, and the first internal gear 133 is rotationally driven by the outer rotor 123 in the same direction as the rotational direction of the first sun gear 131. For this reason, the screw bit 119 is rotated at a high speed with a reduction ratio when the first sun gear 131 and the first internal gear 133 rotate together with the spindle 115.

  On the other hand, when the screw is seated on the workpiece and the load increases, the reaction force of the rotational driving force received by the first internal gear 133 increases. Then, since the driving force of the outer rotor 123 is small, the rotational force by the outer rotor 123 is lost to the reaction force, and the first internal gear 133 tends to be rotated in the reverse direction. As a result, the one-way clutch 151 is operated to lock the first internal gear 133 with respect to the fixed outer ring portion 158. For this reason, the screw bit 119 together with the spindle 115 is rotated at a low speed at a reduction ratio when only the first sun gear 131 rotates. The low-speed rotation state of the spindle 115 is detected by, for example, a current value. That is, the current detector detects that the driving current value of the outer rotor 123 has reached the specified current value. Upon receipt of this detection signal, the motor control device (controller) stops the energization for driving the outer rotor 123, thereby protecting it from burning. The reduction ratio when both the first sun gear 131 and the first internal gear 133 rotate and the reduction ratio when only the first sun gear 131 rotates are the “first and second reduction ratios” in the present invention. Correspond.

  According to the present embodiment, the spindle 115 can be rotated at a high speed in a low load state with a small tightening torque, and the spindle 115 can be rotated at a low speed in a high load state with an increased tightening torque. Thereby, shortening of screw tightening work and high precision can be realized. Further, according to the present embodiment, the torque output by outer rotor 123 can be made lower than the torque output by inner rotor 121, and thus outer rotor 123 can be reduced in size.

(Fourth embodiment of the present invention)
Next, a fourth embodiment of the present invention will be described with reference to FIGS. In this embodiment, in the rechargeable screw driver 101, the first sun gear 131 of the planetary gear mechanism 113 is driven by the inner rotor 121, thereby rotating the spindle 115 (screw bit 119) via the planetary gear mechanism 113. On the other hand, the cooling fan 165 is driven by the outer rotor 123. Except for the above, the two-way one-way clutch 151 is omitted, and in the planetary gear mechanism 113, the first internal gear 133 and the second internal gear 141 are integrally formed and fixed to the gear housing 107 side. In addition, except for the fact that the outer peripheral region of the inner stator 125A is held by the holding member 126, the configuration is substantially the same as in the first embodiment, and therefore, the same reference numerals are given and description thereof is omitted.

  At one end portion (front end portion) of the outer rotor 123 in the long axis direction, a cylindrical fan housing portion 124 extending forward (on the planetary gear mechanism 113 side) from the front end portions of the outer stator 125B and the inner rotor 121 is formed. A cooling fan 165 for cooling the motor is accommodated and fixed in the fan accommodating portion 124. The fan accommodating portion 124 corresponds to an “extending region” in the present invention. The cooling fan 165 corresponds to “an actuating member other than the tip tool” and “fan” in the present invention.

  In the present embodiment, the current value or the like of the drive motor 111 is monitored, and when the heat generation of the drive motor 111 is small, such as when there is no load, the cooling fan 165 is stopped, and the drive motor 111 is When the heat generation increases, the outer rotor 123 is driven and the cooling fan 165 is driven.

According to the present embodiment, the cooling fan 165 can be driven by the outer rotor 123 separately from the driving of the spindle 115 by the inner motor 121, so that the cooling can be performed regardless of the working state of the spindle 115 (screw bit 119). The fan 165 can be always driven at the maximum number of rotations. For this reason, the cooling effect | action of the drive motor 111 improves and it can protect from burning.
Further, since the inner rotor 121 is dedicated to driving the spindle 115, the output of the inner rotor 121 is improved by the amount that the cooling fan 165 is not driven. In addition, when the heat generated by the drive motor 111 is small, the cooling fan 165 can be stopped to suppress noise generation.

  Further, according to the present embodiment, since the motor is arranged coaxially with the spindle 115 that is the output shaft, each member of the inner rotor 121, the inner and outer stators 125A and 125B, and the outer rotor 123 is combined with one cooling fan 165. While being able to cool simultaneously, it becomes possible to mount a comparatively large cooling fan without enlarging the shape of the machine, and it is easy to obtain a cooling effect.

(Fifth embodiment of the present invention)
Next, a fifth embodiment of the present invention will be described with reference to FIG. This embodiment is a modification of the fourth embodiment. In addition to mounting the motor cooling fan 165 on the outer rotor 123, the motor rotor cooling fan 167 is also mounted on the inner rotor 121. Unlike the fourth embodiment, the other configurations are the same as those of the fourth embodiment. The cooling fan 167 driven by the inner rotor 121 is disposed at a rear position at the rear end portion of the inner rotor 121 with respect to the rear end surface of the inner stator 125A. The cooling fans 165 and 167 correspond to “an actuating member other than the tip tool” and “fan” in the present invention.

Therefore, according to the fifth embodiment, since the motor cooling action is performed by the cooling fan 167 even during normal work by rotating the spindle 115 by driving the inner rotor 121, the driving period of the outer rotor 123 can be reduced. it can.
Further, the current value of the drive motor 111 is monitored, and the cooling fan 165 can be driven by the outer rotor 123 and the cooling capacity can be increased when the motor is likely to burn out, such as when the load is high. It can be suitably applied to a tightening tool that performs work in a loaded state. Further, since the cooling fan 165 driven by the outer rotor 123 is used only in a high load state, it is easy to secure a screw tightening work amount per charge.

  In addition, since the motor is arranged coaxially with the spindle 115 as the output shaft, a relatively large cooling fan can be mounted without increasing the shape of the machine as in the case of the fourth embodiment. Thus, it is easy to obtain a cooling effect.

  Although illustration is omitted for convenience, it is possible to employ a configuration in which the dust suction fan is driven by one or both of the inner rotor 121 and the outer rotor 123. For example, a dust collector for collecting dust generated when a drill bit is attached to the spindle 115 and a workpiece is drilled may be provided. The dust suction fan is provided as a suction force generating means for sucking dust generated by drilling. Therefore, it is possible to rationally construct an electric tool with a dust collecting device by driving the dust suction fan as the suction force generating means by either one or both of the inner rotor 121 and the outer rotor 123. .

  In addition, although each embodiment mentioned above demonstrated taking the screw driver as an example as an electric tool, not only the tightening tool used for tightening work, such as a screw, but also the drill used for drilling work, the chiseling work, and the drilling work. The present invention may be applied to a used hammer, a hammer drill, a circular saw for woodworking or metalworking used for cutting work, an electric cutter, or the like.

101 Rechargeable screwdriver (electric tool)
103 Main body (tool body)
105 Motor housing 105A Holding portion 107 Gear housing 109 Hand grip 109a Trigger 110 Battery pack 111 Drive motor (motor, dual rotor motor)
113 Planetary gear mechanism (reduction mechanism)
115 spindle (output shaft)
117 Bit holder 119 Screw bit (tip tool)
121 Inner rotor 121a Inner rotor shaft 121b Magnet 123 Outer rotor 123a Communication window 123b Magnet 124 Fan housing portion 125A Inner rotor stator 125A1 Yoke portion 125A2 Teeth portion 125a Inner rotor drive coil 125B Outer rotor stator 125B1 York portion 125B2 Teeth portion 125b Outer rotor drive coil 125c Pin Element)
126 Holding member 127, 128, 129 Bearing 127A Bearing housing 127a Part 131 First sun gear 133 First internal gear 135 First planetary gear 137 First carrier 139 Second sun gear 141 Second internal gear 143 Second planetary gear 145 Second carrier 147 Overload clutch 151 Two-way one-way clutch 152 Power transmission member 153 Power transmission portion 155 Power reception portion 157 Power reception member 157a Planar region 158 Fixed outer ring portion 159 Lock pins 161, 163, 165, 167 Cooling fan

Claims (25)

A power tool that drives a tip tool by a motor and thereby performs a predetermined processing operation on a workpiece,
The motor includes an inner rotor, an outer rotor, a first stator including an inner rotor driving coil that drives the inner rotor, and a second stator including an outer rotor driving coil that drives the outer rotor, and the inner rotor and the An electric tool characterized in that the outer rotor is configured as a dual rotor motor arranged coaxially with each other. The electric tool according to claim 1,
A housing for housing the dual motor;
An inner motor is constituted by the inner rotor and the first stator, and an outer motor is constituted by the outer rotor and the second stator,
The electric motor characterized in that the inner motor and the outer motor are disposed in the housing in a state shifted in the long axis direction, and a space is formed between an outer peripheral region of the inner motor and the housing. . The electric tool according to claim 2,
In the inner motor, an outer peripheral area of the first stator is fixed to the housing in the space directly or via a holding member. The electric tool according to claim 2 or 3,
The electric power tool, wherein the first stator and the second stator overlap with each other in a state in which the first stator and the second stator are in contact with each other in a radial direction intersecting the major axis direction, and are coupled to each other in the overlapping region. The electric tool according to claim 4,
The electric power tool characterized in that the first stator and the second stator are coupled by a pin in the overlapping region. The electric tool according to claim 4,
The power tool, wherein the first stator and the second stator have the overlapping region joined together by a resin layer. The electric tool according to claim 2,
The outer motor is configured as an axial gap motor arranged so that the outer rotor and the second stator face each other in the long axis direction. The electric tool according to claim 7,
The electric power tool, wherein the first stator and the second stator partially overlap in the major axis direction and are coupled to each other in the overlapping region. The power tool according to claim 8,
In the outer motor, an outer peripheral region of the second stator is fixed by the housing. The electric tool according to any one of claims 1 to 9,
The power tool, wherein the tip tool is driven using both the inner rotor and the outer rotor. The electric tool according to any one of claims 1 to 9,
One of the inner rotor and the outer rotor is used to drive the tip tool, and the other is used to drive an operating member other than the tip tool. The electric tool according to claim 10,
A reduction mechanism,
The dual rotor motor is configured to drive the tip tool via the speed reduction mechanism,
The reduction mechanism has at least first and second reduction ratios, and the first and second reduction ratios are switched by switching at least one of the inner rotor and the outer rotor between a driving state and a stopped state. The electric tool characterized by performing. The power tool according to claim 12,
The reduction ratio switching is performed according to any one of a current value, torque, rotation speed, and temperature of the dual rotor motor. The electric tool according to claim 12 or 13,
An electric tool characterized by changing the first and second reduction ratios to change the output torque output to the tip tool. The electric tool according to claim 12 or 13,
A power tool characterized in that the rotational speed of the tip tool is changed by switching the first and second reduction ratios. The electric tool according to claim 14,
An electric tool characterized by intermittently changing the output torque of the tip tool by intermittently driving the other in a state where one of the inner rotor and the outer rotor is continuously driven. The electric tool according to any one of claims 12 to 16,
The speed reduction mechanism is constituted by a planetary gear mechanism,
The planetary gear mechanism includes a sun gear and an internal gear arranged coaxially with each other, and a planetary gear that meshes and engages with both the sun gear and the internal gear and revolves around the sun gear,
The internal gear is connected to the outer rotor, the sun gear is connected to the inner rotor,
An electric motor characterized in that a relative rotational difference between the sun gear and the internal gear is controlled by driving control of the outer rotor or inner rotor, thereby changing a revolving speed of the planetary gear to switch a reduction ratio. tool. The power tool according to claim 17,
An electric tool characterized in that the inner rotor is driven at all times. The power tool according to claim 17,
An electric tool characterized in that the outer rotor is driven at all times. The power tool according to claim 17,
Between the outer rotor and the internal gear, or between the inner rotor and the sun gear, torque is transmitted from the outer rotor and the internal gear side to the tip tool side, but in the opposite direction, torque is transmitted. Has a clutch that does not transmit
The power tool according to claim 1, wherein the clutch locks the rotation of the internal gear or the sun gear regardless of the rotation of the outer rotor or the inner rotor according to the torque acting on the tip tool. The electric tool according to claim 11,
The operating member other than the tip tool is a rotatable fan,
One of the inner rotor and the outer rotor drives the tip tool, and the other drives the fan. The power tool according to claim 21, wherein
The outer rotor has an extended region in which one end portion in the long axis direction extends longer in the long axis direction than one end portion in the long axis direction of the second stator and the inner rotor,
The electric tool according to claim 1, wherein the fan is disposed inside an extension region of the outer rotor. The electric tool according to claim 21 or 22,
The fan is a cooling fan for cooling the dual rotor motor, and is configured to be driven at all times. The electric tool according to any one of claims 21 to 23,
The electric fan is a cooling fan for cooling the dual rotor motor, and is configured to be intermittently driven according to at least one of temperature, rotational speed, and torque of the dual rotor motor. tool. The electric tool according to claim 21 or 22,
The fan is a dust-absorbing fan that absorbs dust generated in a machining operation, and is configured to be driven in accordance with a dust-absorbing request.

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