JP5440765B2 - Impact tools - Google Patents

Description

  The present invention relates to an impact tool that is driven by a motor and realizes a novel striking mechanism.

  The impact tool drives the rotary impact mechanism using a motor as a drive source, and intermittently transmits the rotary impact force to the tip tool by applying rotation and impact to the anvil to perform operations such as screw tightening. As a motor to be used, a brushless DC motor has been widely used. The brushless DC motor is, for example, a DC (direct current) motor without a brush (rectifying brush), and is driven by an inverter circuit using a coil (winding) on the stator side and a magnet (permanent magnet) on the rotor side. The rotor is rotated by sequentially energizing the predetermined power to a predetermined coil. The inverter circuit is configured using a large-capacity output transistor such as an FET (Field Effect Transistor) or an IGBT (Insulated Gate Bipolar Transistor), and is driven with a large current. A brushless DC motor is excellent in torque characteristics as compared with a brushed DC motor, and can tighten a screw, a bolt, or the like on a workpiece by a stronger force.

  As an example of an impact tool using a brushless DC motor, for example, the technique of Patent Document 1 is known. In Patent Document 1, a hammer that has a continuously rotating impact mechanism portion and engages movably in the direction of the rotation axis of the spindle when a rotational force is applied to the spindle via a power transmission mechanism portion (deceleration mechanism portion). Rotates and rotates the anvil that contacts the hammer. The hammer and the anvil each have two hammer protrusions (striking parts) arranged symmetrically with each other at two locations on the plane of rotation, and these protrusions are in positions that mesh with each other in the rotation direction. Rotating impact force is transmitted by the meshing. The hammer is slidable in the axial direction with respect to the spindle in a ring region surrounding the spindle, and an inverted V-shaped (substantially triangular) cam groove is provided on the inner peripheral surface of the hammer. A V-shaped cam groove is provided in the axial direction on the outer peripheral surface of the spindle, and the hammer rotates via a ball (steel ball) inserted between the cam groove and the inner peripheral cam groove of the hammer. To do.

JP 2009-72888 A

  In the conventional power transmission mechanism, the spindle and the hammer are held via a ball disposed in the cam groove, and the hammer can be moved backward in the axial direction with respect to the spindle by a spring disposed at the rear end. It is configured. Therefore, the number of parts of the spindle and the hammer portion increases, and it is necessary to consider so as to improve the mounting accuracy between the spindle and the hammer, so that the manufacturing cost is high.

  On the other hand, in the conventional impact tool, in order to control the impact mechanism so that it does not operate (that is, no impact occurs), some kind of contrivance is required, such as providing a mechanism for controlling the retracting movement of the hammer. With the technique of Document 1, the impact tool could not be used as a so-called drill mode. Furthermore, even if a drill mode for controlling the backward movement of the hammer is realized, it is necessary to separately provide a clutch mechanism in order to realize a clutch operation for interrupting power transmission when a predetermined tightening torque is achieved. In order to realize the drill mode and the drill mode with clutch for impact tools, the cost was increased.

  Furthermore, in the technique of Patent Document 1, when the hammer is struck, the driving power supplied to the motor is constant regardless of the load state of the tip tool. Therefore, even a light load state is hit with a high tightening torque, and excessive electric power is supplied to the motor, resulting in unnecessary power consumption. Further, by hitting with a high tightening torque, a so-called cam-out phenomenon is likely to occur such that the screw advances excessively during screw tightening and the tip tool moves away from the screw head.

  The present invention has been made in view of the above background, and an object of the present invention is to provide an impact tool in which an impact mechanism is realized by a simple mechanism hammer and anvil.

  Another object of the present invention is to provide an impact tool capable of performing a fastening operation by driving a hammer and anvil having a relative rotation angle of less than 360 degrees by devising a motor driving method. .

  Still another object of the present invention is to provide a multi-use impact tool that can be used by switching between a drill mode and an impact mode.

Of the inventions disclosed in the present application, typical features will be described as follows. According to one feature of the present invention, is arranged a motor, a reduction mechanism for reducing the rotational force of the motor, and the hammer which is capable of continuous rotation is connected to the output portion of the speed reduction mechanism, the front side of the hammer hammer An impact tool in which a rotational force or a striking force is applied by an anvil that rotates the tip tool, and an output part of the speed reduction mechanism, a hammer, and a central axis of the anvil are arranged coaxially with the rotational axis of the motor , hammer has a fitting portion formed on the center axis 1 or more sets of projection projecting from the body portion in the radial outer side or axially (uneven portion), the anvil is radially outward from the body portion Or it has a fitting part which fits one or more sets of protrusion parts (concave-convex part) which protrudes in an axial direction, and a fitting part of a hammer part, and an impact part where at least one protrusion part of an anvil and a hammer collides mutually With an anvil and a hammer Out portion is relatively less than 60 degrees 360 degrees or more, preferably from anvil and the hammer so as to be rotatable at the maximum rotational angle of less than 360 degrees by 180 degrees or more. As the speed reduction mechanism, for example, a planetary gear mechanism can be used. The rotation shaft of the motor is connected to the sun gear of the planetary gear mechanism, and the hammer is fixed so as to connect the rotation shafts of the plurality of planetary gears of the planetary gear mechanism. It is preferable that the hammer and the anvil are each made of an integral metal structure.

According to another feature of the invention, the hammer is intermittently hit against the anvil by rotating the motor in the forward and reverse directions. The hammer and the anvil are provided with two blade portions extending radially outward from the main body portion, and the protruding portion is formed on the blade portion. Each of the blades is formed with two projecting portions having striking surfaces, and the plurality of striking surfaces formed on the hammer projecting portions collide simultaneously with the plurality of striking surfaces formed on the projecting portions of the anvil. Ru is configured. Motors and the hammer are connected via a planetary gear reduction mechanism, the hammer is configured to also serve as the function of planet carrier for holding a plurality of planetary gears of the planetary gear reduction mechanism.

  According to still another aspect of the present invention, there is provided an impact tool comprising a motor, a hammer that is connected to the output of the motor and driven in a pulsed manner, and an anvil that is struck in the rotational direction by the hammer. As a run-up rotation before hitting the anvil, it was possible to rotate 180 degrees or more. Also, the hammer is almost immovable in the axial direction with respect to the anvil.

  According to the present invention, the anvil and the hammer are formed so that the protrusion of the anvil and the hammer can be rotated at a maximum rotation angle of 60 degrees or more and less than 360 degrees, and the hammer is continuously rotated relative to the anvil. Since there is no need to provide a conventional cam mechanism, a mechanism that retreats in the axial direction, a spring, etc. in the impact tool, it is possible to realize a compact striking mechanism with a short axial longitudinal length. Can do. In addition, since the hammer and the anvil are not relatively continuously rotated, it is possible to easily cope with continuous driving in the drill mode, and an impact tool that can simultaneously realize the drill mode and the impact mode can be realized.

According to the present invention, the speed reduction mechanism is a planetary gear mechanism, the rotation shaft of the motor is connected to the sun gear of the planetary gear mechanism, and the hammer is fixed so as to connect the rotation shafts of the plurality of planetary gears of the planetary gear mechanism. Therefore, it is possible to reduce the number of parts and the axial length required for the hammer portion. Further, since the output shaft of the speed reduction mechanism and the hammer are integrally formed, the striking mechanism can be configured compactly. Furthermore, since the hammer and the anvil are each made of a metal integrated structure, a striking mechanism that is strong in strength can be realized. Further, since the hammer and the anvil are relatively simple in shape, the manufacturing cost can be reduced.

  According to the present invention, since the hammer is intermittently hit against the anvil by rotating the motor in the forward direction and the reverse direction, the impact mechanism can be realized only by devising the motor driving method. Furthermore, since the hammer and the anvil are provided with two blade portions extending radially outward from the main body portion, and the protruding portion is formed on the blade portion, the protruding portion can be easily formed by integral molding. Moreover, since the diameter of a main-body part can be made small by providing a blade | wing part, weight reduction of a hammer and an anvil can be achieved. Further, each of the blade portions is formed with two projecting portions having striking surfaces, and the plurality of striking surfaces formed on the projecting portion of the hammer collide simultaneously with the plurality of striking surfaces formed on the projecting portions of the anvil. Therefore, if a plurality of striking surfaces are arranged in axisymmetric positions, the bias of the striking torque is reduced, and the vibration and reaction transmitted to the impact tool at the time of striking are reduced, thereby realizing an easy-to-use impact tool.

According to the present invention, the striking part of the anvil and the hammer relatively rotate at a maximum rotation angle of 180 degrees or more and less than 360 degrees, so that a sufficient reversing angle of the motor can be ensured in combination with the reduction ratio in the reduction mechanism. Can be hit with a strong torque. Further, since the running rotation (acceleration section) before the hammer hits the anvil has a relative rotation of 180 degrees or more, the anvil can be efficiently hit with the hammer. Furthermore, since the hammer is almost immovable in the axial direction with respect to the anvil , the hammer does not give an axial striking force to the tip tool, and even if a wood screw or the like is tightened on the wood, Can be prevented from being damaged. In addition, backlash is unlikely to occur in the anvil.
The above and other objects and novel features of the present invention will become apparent from the following description and drawings.

It is a longitudinal section showing the whole structure of impact tool 1 concerning the example of the present invention. It is a perspective view which shows the external appearance of the impact tool 1 which concerns on the Example of this invention. It is an expanded sectional view of the vicinity of the striking mechanism 40 of FIG. It is a perspective view of the cooling fan 18 of FIG. It is a functional block diagram which shows the drive control system of the motor 3 of the impact tool which concerns on the Example of this invention. It is a figure which shows the shape of the hammer 151 and the anvil 156 which concern on the basic composition (2nd Example) of this invention. It is a figure which shows the hammering operation | movement of the hammer 151 of FIG. 6, and the anvil 156, and is sectional drawing which showed the motion of 1 rotation in 6 steps. It is a perspective view which shows the shape of the hammer 41 and the anvil 46 of FIG. It is a perspective view from another angle which shows the shape of the hammer 41 and the anvil 46 of FIG. It is a figure which shows the hit | damage operation | movement of the hammer 41 and the anvil 46 shown in FIG. It is a figure which shows the trigger signal at the time of operation | movement of the impact tool 1, the drive signal of an inverter circuit, the rotational speed of the motor 3, and the hammering situation of the hammer 41 and the anvil 46. FIG. It is a flowchart which shows the drive control procedure of the motor 3 which concerns on the Example of this invention. It is a figure for demonstrating the drive mode of the hammer 41 in a present Example, and is the graph which showed the electric current and rotation speed which are applied to the motor in a continuous drive mode . It is a drive control procedure of the motor which concerns on the Example of this invention, Comprising: It is a flowchart which shows the control procedure in pulse mode (1). It is a graph which shows the relationship between the rotation speed of the motor 3, and elapsed time, and the relationship between the electric current value supplied to the motor 3, and elapsed time. It is a drive control procedure of the motor 3 which concerns on the Example of this invention, Comprising: It is a flowchart which shows the control procedure in pulse mode (2).

  Embodiments of the present invention will be described below with reference to the drawings. In the following description, the front and rear, front and rear, and left and right directions will be described as the directions shown in FIGS.

  FIG. 1 is a diagram showing an internal structure of an impact tool 1 as an embodiment of an impact tool according to the present invention. The impact tool 1 uses a rechargeable battery pack 30 as a power source, drives the striking mechanism 40 using the motor 3 as a driving source, and applies rotation and striking to the anvil 46 as an output shaft, thereby providing a tip tool (not shown) such as a driver bit. Transmitting continuous rotational force and intermittent striking force to the screw and tightening bolts.

  The motor 3 is a brushless DC motor, and is accommodated in a cylindrical body portion 6a of a housing 6 having a substantially T-shape when viewed from the side. The housing 6 can be divided into two substantially right and left members having a substantially symmetrical shape, and these members are fixed by a plurality of screws. Therefore, a plurality of screw bosses 20 are formed in one of the divided housings 6 (left housing in the present embodiment), and a plurality of screw holes (not shown) are formed in the other (right housing). The rotating shaft 19 of the motor 3 is rotatably held by a bearing 17b on the rear end side of the body portion 6a and a bearing 17a provided near the center portion. A substrate on which six switching elements 10 are mounted is provided behind the motor 3, and the motor 3 is rotated by performing inverter control with these switching elements 10. A rotational position detection element 58 such as a Hall element or Hall IC is mounted on the front side of the substrate 7 in order to detect the position of the rotor 3a.

  A trigger switch 8 and a forward / reverse switching lever 14 are provided in an upper portion of a grip portion 6b that integrally extends substantially perpendicularly from the body portion 6a of the housing 6, and the trigger switch 8 is biased by a spring (not shown) to be gripped by the grip portion 6b. A trigger operation portion 8a protruding from the center is provided. A control circuit board 9 having a function of controlling the speed of the motor 3 by the trigger operation portion 8a is accommodated below the grip portion 6b. A battery pack 30 in which a plurality of battery cells such as nickel metal hydride and lithium ions are accommodated is detachably attached to the battery holding portion 6 c formed below the grip portion 6 b of the housing 6.

  A cooling fan 18 that is attached to the rotary shaft 19 and rotates in synchronization with the motor 3 is provided in front of the motor 3. The cooling fan 18 sucks air from the air intakes 26a and 26b provided at the rear of the body portion 6a. The sucked air is discharged to the outside of the housing 6 through a plurality of slits 26c (see FIG. 2) formed in the body portion 6a of the housing 6 and in the vicinity of the outer peripheral side of the cooling fan 18 in the radial direction.

The striking mechanism 40 is composed of two parts, an anvil 46 and a hammer 41, and the hammer 41 is fixed so as to connect the rotation shafts of a plurality of planetary gears of the planetary gear reduction mechanism 21. Unlike a known impact mechanism that is widely used at present, the hammer 41 does not have a cam mechanism having a spindle, a spring, a cam groove, a ball, and the like. The anvil 46 and the hammer 41 are connected so that only a relative rotation of less than one rotation can be performed by a fitting shaft and a fitting hole formed near the rotation center. The anvil 46 is formed integrally with an output shaft portion on which a tip tool (not shown) is mounted, and a mounting hole 46a having a hexagonal cross section in the axial direction and the vertical plane is formed at the front end. The rear side of the anvil 46 is connected to the fitting shaft of the hammer 41 and is held rotatably with respect to the case 5 by the metal bearing 16a near the center in the axial direction. The detailed shapes of the anvil 46 and the hammer 41 will be described later.

The case 5 is formed by metal integral molding for accommodating the striking mechanism 40 and the planetary gear speed reduction mechanism 21, and is attached to the front side of the housing 6. Also, the outer peripheral side of the case 5, while preventing the transfer of heat, is covered with resin cover 11 in order to fulfill a shock absorbing effect and the like. A sleeve 15 for attaching / detaching a tip tool is provided at the tip of the anvil 46.

  When the trigger operation unit 8a is pulled and the motor 3 is started, the rotation of the motor 3 is decelerated by the planetary gear speed reduction mechanism 21 and the hammer 41 rotates at a rotation rate of a predetermined ratio with respect to the rotation rate of the motor 3. . When the hammer 41 rotates, the rotational force is transmitted to the anvil 46, and the anvil 46 starts rotating at the same speed as the hammer 41. When the force applied to the anvil 46 increases due to the reaction force received from the tip tool side, the control unit described later detects an increase in the tightening reaction force, and before the motor 3 stops rotating and enters the locked state, the hammer 41 The hammer 41 is driven continuously or intermittently while changing the drive mode.

  FIG. 2 is a perspective view showing an appearance of the impact tool 1 of FIG. The housing 6 is composed of three parts (6a, 6b, 6c), and a cooling air discharge slit 26c is formed in the body portion 6a in the vicinity of the outer peripheral side of the cooling fan 18 in the radial direction. A control panel 31 is provided on the upper surface of the battery holding portion 6c. Various operation buttons, display lamps, and the like are arranged on the control panel 31. For example, a switch for turning on / off the LED light 12 and a button for checking the remaining amount of the battery pack are arranged. Further, a toggle switch 32 for switching the drive mode (drill mode, impact mode) of the motor 3 is provided on the side surface of the battery holding portion 6c. Each time the toggle switch 32 is pressed, the drill mode and the impact mode are alternately switched.

The battery pack 30, the release button 30 a is provided, by moving the battery pack 30 forward while pressing the release button 30 a located on the left and right sides, it is possible to remove the battery pack 30 from the battery holding portion 6c . A detachable metal belt hook 33 is provided on the left and right sides of the battery mounting portion 6c. In FIG. 2, it is attached to the left side of the impact tool 1, but it is also possible to remove the belt hook 33 and attach it to the right side of the impact tool 1. A strap 34 is attached near the rear end of the battery attachment portion 6c.

  FIG. 3 is an enlarged cross-sectional view of the vicinity of the striking mechanism 40 of FIG. The planetary gear speed reduction mechanism 21 is a planetary type, and a sun gear 21a connected to the tip of the rotating shaft 19 of the motor 3 serves as a drive shaft (input shaft), and a plurality of outer gears 21d fixed to the body portion 6a. Planetary gear 21b rotates. The plurality of rotating shafts 21c of the planetary gear 21b are held by a hammer 41 having a planetary carrier function. The hammer 41 rotates as a driven shaft (output shaft) of the planetary gear speed reduction mechanism 21 at a predetermined reduction ratio in the same direction as the motor 3. How much the speed reduction ratio is set may be set appropriately based on factors such as the main fastening target (screw or bolt), the output of the motor 3 and the magnitude of the required fastening torque. The reduction ratio is set so that the rotation speed of the hammer 41 is about 1/8 to 1/15 with respect to the rotation speed of the motor 3.

  An inner cover 22 is provided on the inner peripheral side of the two screw bosses 20 inside the body portion 6a. The inner cover 22 is a member manufactured by integral molding of synthetic resin such as plastic. A cylindrical portion is formed on the rear side, and a bearing 17a that rotatably fixes the rotating shaft 19 of the motor 3 at the cylindrical portion. Hold. In addition, a cylindrical step portion having two different diameters is provided on the front side of the inner cover 22, and a ball type bearing 16b is provided on the smaller step portion, and the larger cylindrical step portion is provided. Part of the outer gear 21d is inserted into the part from the front side. The outer gear 21d is non-rotatably attached to the inner cover 22, and the inner cover 22 is non-rotatably attached to the body portion 6a of the housing 6. Therefore, the outer gear 21d is fixed in a non-rotating state. Further, a flange portion having a large outer diameter is provided on the outer peripheral portion of the outer gear 21 d, and an O-ring 23 is provided between the flange portion and the inner cover 22. Grease (not shown) is applied to the rotating portions of the hammer 41 and the anvil 46, and the O-ring 23 seals the grease so that it does not leak to the inner cover 22 side.

A characteristic feature of this embodiment is that the hammer 41 has the function of a planet carrier that holds the plurality of rotating shafts 21c of the planetary gear 21b. Therefore, the rear end portion of the hammer 41 extends to the inner peripheral side of the inner ring of the bearing 16b . Further, the inner peripheral portion on the rear side of the hammer 41 is disposed in a cylindrical internal space that houses a sun gear 21 a attached to the rotating shaft 19 of the motor 3. Near the front side central axis of the hammer 41, the fitting shaft 41a is formed to protrude axially forward, the fitting shaft 41a is fitted to the cylindrical fitting bore 46f formed near the rear side the central axis of the anvil 46 Match. Incidentally, the fitting shaft 41a and the fitting holes 46f are those in which both are pivotally supported so as to be relatively rotated.

  FIG. 4 is a perspective view of the cooling fan 18. The cooling fan 18 is manufactured by an integrated structure of synthetic resin such as plastic. A through-hole 18a through which the rotation shaft 19 passes is formed at the rotation center, and a cylindrical portion 18b that covers the rotation shaft 19 by a predetermined distance in the axial direction and secures a predetermined distance from the rotor 3a is formed. A plurality of fins 18c are formed on the outer peripheral side. An annular portion is provided on the front and rear sides of the fin 18c, and the air sucked from the rear in the axial direction is not limited to the rotation direction of the cooling fan 18, and the air is drawn from the plurality of openings 18d formed near the outer periphery. Drain outward in the direction. The cooling fan 18 functions as a so-called centrifugal fan, and is directly connected to the rotating shaft 19 of the motor 3 without the planetary gear reduction mechanism 21, so that the cooling fan 18 is rotated at a sufficiently higher number of rotations than the hammer 41. Therefore, a sufficient air volume can be ensured.

  Next, the configuration and operation of the drive control system of the motor 3 will be described with reference to FIG. FIG. 5 is a block diagram showing the configuration of the drive control system of the motor 3. In this embodiment, the motor 3 is a three-phase brushless DC motor. This brushless DC motor is a so-called inner rotor type, and includes a rotor (rotor) 3a including a plurality of sets (two sets in this embodiment) of permanent magnets (magnets) including N poles and S poles. In order to detect the rotational position of the rotor 3a, a stator 3b composed of three-phase stator windings U, V, and W connected in a star connection is arranged at predetermined intervals in the circumferential direction, for example, at an angle of 60 °. The three rotational position detecting elements (Hall elements) 58 are provided. Based on the position detection signals from these rotational position detection elements 58, the energization direction and time for the stator windings U, V, W are controlled, and the motor 3 rotates. The rotational position detection element 58 is provided at a position facing the permanent magnet 3 c of the rotor 3 a on the substrate 7.

  The electronic elements mounted on the substrate 7 include six switching elements Q1 to Q6 such as FETs connected in a three-phase bridge format. The gates of the six switching elements Q1 to Q6 that are bridge-connected are connected to a control signal output circuit 53 mounted on the control circuit board 9, and the drains or sources of the six switching elements Q1 to Q6 are It is connected to the stator windings U, V, W that are star-connected. As a result, the six switching elements Q1 to Q6 perform a switching operation by the switching element drive signals (drive signals such as H4, H5, and H6) input from the control signal output circuit 53 and are applied to the inverter circuit 52. Electric power is supplied to the stator windings U, V, and W using the DC voltage of the battery pack 30 as three-phase (U-phase, V-phase, and W-phase) voltages Vu, Vv, and Vw.

  Of the switching element drive signals (three-phase signals) for driving the gates of the six switching elements Q1 to Q6, the three negative power supply side switching elements Q4, Q5, Q6 are converted into pulse width modulation signals (PWM signals) H4, The pulse width (duty ratio) of the PWM signal is supplied as H5 and H6 and based on the detection signal of the operation amount (stroke) of the trigger operation unit 8a of the trigger switch 8 by the calculation unit 51 mounted on the control circuit board 9. The amount of electric power supplied to the motor 3 is adjusted by changing, and the start / stop of the motor 3 and the rotation speed are controlled.

  Here, the PWM signal is supplied to any one of the positive power supply side switching elements Q1 to Q3 or the negative power supply side switching elements Q4 to Q6 of the inverter circuit 52, and the switching elements Q1 to Q3 or the switching elements Q4 to Q6 are switched at high speed. As a result, the power supplied to the stator windings U, V, W from the DC voltage of the battery pack 30 is controlled. In this embodiment, since the PWM signal is supplied to the negative power supply side switching elements Q4 to Q6, the power supplied to each stator winding U, V, W is adjusted by controlling the pulse width of the PWM signal. Thus, the rotation speed of the motor 3 can be controlled.

  The impact tool 1 is provided with a forward / reverse switching lever 14 for switching the rotational direction of the motor 3, and the rotational direction setting circuit 62 switches the rotational direction of the motor each time a change in the forward / reverse switching lever 14 is detected. The control signal is transmitted to the calculation unit 51. Although not shown, the arithmetic unit 51 is a central processing unit (CPU) for outputting a drive signal based on the processing program and data, a ROM for storing the processing program and control data, and for temporarily storing data. RAM, a timer, and the like.

The calculation unit 51 forms a drive signal for alternately switching predetermined switching elements Q1 to Q6 based on output signals of the rotation direction setting circuit 62 and the rotor position detection circuit 54, and outputs the drive signal as a control signal. Output to the circuit 53. As a result, the predetermined windings of the stator windings U, V, and W are alternately energized to rotate the rotor 3a in the set rotation direction. In this case, the drive signal applied to the negative power supply side switching elements Q4 to Q6 is output as a PWM modulation signal based on the output control signal of the applied voltage setting circuit 61. The current value supplied to the motor 3 is measured by the current detection circuit 59, and the value is fed back to the calculation unit 51 to be adjusted to the set driving power. The PWM signal may be applied to the positive power supply side switching elements Q1 to Q3.

The control unit 50 mounted on the control circuit board 9 is connected to a striking impact detection sensor 56 for detecting the magnitude of impact generated in the anvil 46, and the output is sent to the calculation unit 51 via the striking impact detection circuit 57. Entered. The strike impact detection sensor 56 can be realized by a strain gauge or the like attached to the anvil 46, when the tightening to the specified torque by using an output of the striking impact detection sensor 56 has been completed, even if the motor 3 so as to automatically stop good.

Next, before describing the hammering operation of the hammer 41 and the anvil 46 according to this embodiment, the basic configuration of the hammer and anvil of the present invention and the principle of the hammering operation will be described with reference to FIGS. FIG. 6 is a diagram showing the shapes of the hammer 151 and the anvil 156 according to the basic configuration of the present invention, and has the simplest shape. This shape is also the shape according to the second embodiment of the present invention. The hammer 151 is formed with a pair of protrusions that protrude in the axial direction from the cylindrical main body portion 151b, that is, a protrusion 152 and a protrusion 153. Front side of the main body portion 151b, in the center, the fitting shaft 151a which fits into a fitting hole formed in the rear of the anvil 156 (not shown) is formed, the hammer 151 and the anvil 156 are relatively revolution It is connected so that it can rotate by a predetermined angle of less than (less than 360 degrees). The protrusion 152 functions as a hitting claw, and planar hitting surfaces 152a and 152b are formed on both sides in the circumferential direction. Further, the hammer 151 is formed with a protrusion 153 for balancing the rotation with the protrusion 152. Since the projecting portion 153 functions as a weight portion for balancing rotation, the striking surface is not formed.

A disc portion 151c is formed on the rear side of the main body portion 151b via a connection portion 151d. The space between the body portion 151b and the disc portion 151 c is for arranging the planetary gear 21b of the planetary gear mechanism 21, the disc portion 151 c for holding the rotary shaft 21c of the planetary gear 21b is A through hole 151f is formed. Although not shown, the holding hole for holding the rotating shaft 21c of the body portion 151b of the disc portion 151 planetary also on the side facing the c Lee gear 21b is formed.

The anvil 156 is formed with a mounting hole 156a for mounting the tip tool on the front end side of the cylindrical main body portion 156b, and two protrusions protruding radially outward from the main body portion 156b on the rear side of the main body portion 156b. 157 and 158 are formed. The protruding portion 157 is a hitting claw having hitting surfaces 157a and 157b, and the protruding portion 158 is a weight portion having no hitting surface. Protrusions 157, because it is configured to collide with the projecting portion 152, an outer diameter equal constructed with an outer diameter of the protrusion 152. However, the protrusions 153 and 158 both act as weights and do not collide with any part, so it is important to form and arrange them at positions and sizes that do not interfere with each other. Further, in order to obtain as much relative rotation angle as possible between the hammer 151 and the anvil 156 (however, it is less than one rotation at the maximum), the radial thickness of the protrusions 153 and 158 is reduced to reduce the circumferential direction. By increasing the length, the protrusions 152 and 157 are formed so as to balance the rotation. By setting the relative rotation angle to be large, it is possible to increase the acceleration section (running section) of the hammer when the hammer collides with the anvil, and it is possible to hit with a large amount of energy.

FIG. 7 is a cross-sectional view showing the movement of one rotation in the use state of the hammer 151 and the anvil 156 in six stages. Section is a axial and vertical plane, a cross section including the striking face 152a (Fig. 6). 7 (1), the anvil 156 rotates counterclockwise by being pushed from the hammer 151 while the tightening torque received from the tip tool is small. However, when the tightening torque becomes large and the rotation becomes impossible only by the force pushed from the hammer 151, the hammer 151 is hit by the anvil 156, so that the hammer 151 is reversely rotated in the direction of the arrow 161. Start spinning. In the state shown in (1), the reversal of the motor 3 is started, whereby the protrusion 152 of the hammer 151 is rotated in the direction of the arrow 161, and further the motor 3 is rotated in the reverse direction, as shown in (2). 152 rotates while being accelerated in the direction of the arrow 162 through the outer peripheral side of the protrusion 158. Here, the outer diameter R _a1 of the protruding portion 158 is configured to be smaller than the inner diameter R _h1 of the protruding portion 152, so that they do not collide. Similarly, the outer diameter R _a2 of the protrusion 157 is configured to be smaller than the inner diameter R _h2 of the protrusion 153, and they do not collide. With this positional relationship, the relative rotation angle between the hammer 151 and the anvil 156 can be configured to be greater than 180 degrees, and a sufficient amount of reversal angle of the hammer 151 relative to the anvil 156 can be ensured. it can.

  When the hammer 151 further reversely rotates and reaches the position of FIG. 7 (3) (reverse rotation stop position) as shown by an arrow 163a, the rotation of the motor 3 is stopped for a certain period of time, and then the arrow 163b of the motor 3 Start rotation in the direction (forward rotation direction). It is important that the hammer 151 is reliably stopped at the stop position so as not to collide with the anvil 156 when the hammer 151 is rotated in the reverse direction. It is arbitrary how long the stop position of the hammer 151 is set before the position where the hammer 151 collides with the anvil 156, but it is preferable to make it as large as possible because of the required tightening torque. The stop position does not need to be the same every time, and the reverse rotation angle may be reduced at the initial stage of tightening, and the reverse rotation angle may be set larger as tightening proceeds. If the stop position is made variable in this way, the time required for reverse rotation can be set to the minimum, so that the striking operation can be performed quickly in a short time.

Then, the hammer 151 is further accelerated while passing the position of FIG. 7 (4) in the direction of the arrow 164, and the striking surface 152a of the projecting portion 152 at the position shown in FIG. It collides with the hit surface 157a of the anvil 156. As a result of this collision, a strong rotational torque is transmitted to the anvil 156, and the anvil 156 rotates in the direction indicated by the arrow 166. The position of FIG. 7 (6) is a state in which both the hammer 151 and the anvil 156 are rotated by a predetermined angle from the state shown in FIG. 7 (1), and again from the state of FIG. 7 (1) in FIG. By repeating the operation up to (5), the fastened member is tightened until an appropriate torque is obtained.

As described above, with the hammer 151 and the anvil 156 according to the present invention, an impact tool is realized with a very simple configuration of only the hammer 151 and the anvil 156 as a striking mechanism by using a drive mode in which the motor 3 is rotated in the reverse direction. be able to. In the striking mechanism of this structure, depending on setting of the drive mode of the motor 3 can be rotated as a drill mode. For example, in the drill mode, the anvil 156 can be rotated following the rotation as shown in FIG. 7 (6) simply by rotating the motor 3 from the state of FIG. 7 (5) and rotating the hammer 151 in the forward direction. Therefore, by repeating this, it is possible to fasten a fastened member such as a screw or bolt that requires a small tightening torque.

  Furthermore, since the impact tool 1 according to the present embodiment uses a brushless DC motor as the motor 3, the current value flowing through the motor 3 is obtained from the current detection circuit 59 (see FIG. 5), and the current value is a predetermined value. By detecting a state where the value is larger than the value and stopping the motor 3 by the calculation unit 51, a so-called clutch mechanism that cuts off power transmission after being tightened to a predetermined torque can be realized electronically. Therefore, in the impact tool 1 according to the present embodiment of the present invention, a clutch mechanism in the drill mode can also be realized, and a drill mode without a clutch, a drill mode with a clutch, A multi-use tightening tool with impact mode can be realized.

Next, the detailed structure of the striking mechanism 40 shown in FIGS. 1 and 2 will be described with reference to FIGS. FIG. 8 is a perspective view showing the shapes of the hammer 41 and the anvil 46 according to the first embodiment of the present invention, in which the hammer 41 is seen obliquely from the front and the anvil 46 is seen obliquely from the rear. FIG. 9 is a perspective view showing the shapes of the hammer 41 and the anvil 46. The hammer 41 is a view seen obliquely from the rear, and the anvil 46 is a partial view seen obliquely from the front. The hammer 41 is formed with two blade portions 41c and 41d protruding in a radial direction from the cylindrical main body portion 41b. The blade portions 41 c and 41 d are each formed with a protruding portion that protrudes in the axial direction. The difference from the basic configuration (second embodiment) shown in FIG. 6 is that the blade portions 41 c and 41 d A pair of striking portions and weight portions are formed in each of the above.

  On the blade portion 41c side, the outer peripheral portion is formed in a fan shape, and a protruding portion 42 that protrudes forward in the axial direction from the outer peripheral portion is formed. The fan-shaped portion and the projecting portion 42 function as a striking portion (striking claw) and simultaneously function as a weight portion. The projecting portion 42 is formed with striking surfaces 42a and 42b on both sides in the circumferential direction. The striking surfaces 42a and 42b are both formed in a flat surface, and are appropriately angled so as to make good surface contact with the striking surface to be described later of the anvil 46. On the other hand, the blade portion 41d is formed so that the outer peripheral portion expands in a fan shape, and the shape of the fan portion increases in mass, and serves as a weight portion. In addition, a protruding portion 43 that protrudes forward in the axial direction from the radial center of the blade portion 41d is formed. The protrusion 43 acts as a striking portion (striking claw), and striking surfaces 43a and 43b are formed on both sides in the circumferential direction. The striking surfaces 43a and 43b are both formed in a flat shape, and are given an appropriate angle in the circumferential direction so as to satisfactorily come into surface contact with the striking surface to be described later of the anvil 46.

Near the axis of the body portion 41b, the fitting shaft 41a on the front side to be fitted to the fitting hole 46f of the anvil 46 is formed. On the rear side of the main body portion 41b, two disk portions 44a and 44b and a connection portion 44c for connecting them at two locations in the circumferential direction are formed so as to function as a planet carrier. Through holes 44d are formed at two locations in the circumferential direction of the disk portions 44a and 44b, two planetary gears 21b (see FIG. 3) are disposed between the disk portions 44a and 44b, and the planetary gear 21b. The rotating shaft 21c (see FIG. 3) is mounted in the through hole 44d. A cylindrical portion 44e extending in a cylindrical shape is formed on the rear side of the disk portion 44b. The outer peripheral side of the cylindrical portion 44e is held by the inner ring of the bearing 16b. The sun gear 21a (see FIG. 3) is disposed in the space 44f inside the cylindrical portion 44e. The hammer 41 and the anvil 46 shown in FIG. 8 and FIG. 9 are preferable in terms of strength and weight when manufactured in a metal integrated structure.

  The anvil 46 is formed with two blade portions 46c and 46d protruding in a radial direction from the cylindrical main body portion 46b. A protruding portion 47 that protrudes rearward in the axial direction is formed near the outer periphery of the blade portion 46c. The hitting surfaces 47 a and 47 b are formed on both sides in the circumferential direction of the protrusion 47. On the other hand, a protruding portion 48 protruding rearward in the axial direction is formed in the vicinity of the radial center of the blade portion 46d. The hitting surfaces 48 a and 48 b are formed on both sides in the circumferential direction of the protrusion 48. When the hammer 41 rotates in the forward direction (rotating direction in which a screw or the like is tightened), the striking surface 42a comes into contact with the hit surface 47a, and at the same time, the hit surface 43a comes into contact with the hit surface 48a. Further, when the hammer 41 rotates in the reverse direction (rotating direction for loosening a screw or the like), the striking surface 42b comes into contact with the hit surface 47b, and at the same time, the hit surface 43b comes into contact with the hit surface 48b. The shapes of the protrusions 42, 43, 47, and 48 are determined so that the abutment occurs simultaneously.

  As described above, according to the hammer 41 and the anvil 46 shown in FIGS. 8 and 9, since the impact is performed at two symmetrical positions with respect to the rotating shaft center, the balance at the time of impact is good. Can be configured to be difficult to shake. Further, since the striking surfaces are provided on both sides in the circumferential direction of the projecting portion, the impact operation can be performed not only in the normal rotation but also in the reverse rotation, so that an easy-to-use impact tool can be realized. Further, the hammer 41 hits the anvil 46 only in the circumferential direction, and does not strike the anvil 46 in the axial direction and forward, so that the tool is not pressed against the screw more than necessary, and the wood screw is pressed against the wood. It is advantageous when tightening etc.

  Next, the hammering operation of the hammer 41 and the anvil 46 shown in FIGS. 8 and 9 will be described with reference to FIG. The basic operation is the same as the operation described with reference to FIG. 7, and the difference is that, at the time of hitting, the hitting is performed simultaneously at two hitting surfaces that are substantially axisymmetric instead of one. 10 is a cross section taken along the line AA of FIG. 3. From this cross section, projecting portions 42 and 43 projecting from the hammer 41 in the axial direction, and projecting portion 47 projecting from the anvil 46 in the axial direction. 48 will be understood. The direction of rotation of the anvil 47 during the tightening operation (during forward rotation) is counterclockwise.

FIG. 10A shows a state in which the hammer 41 is reversely rotated to the most reversed position with respect to the anvil 46 (corresponding to the state shown in FIG. 7C). From this state, the hammer 41 is accelerated in the direction of the arrow 91 (positive direction) to collide with the anvil 46. Then, as shown in FIG. 10 (2), the protruding portion 42 passes the outer peripheral side of the protruding portion 48, and at the same time, the protruding portion 43 passes the inner peripheral side of the protruding portion 47. In this way, in order to allow both to pass, the inner diameter R _H2 of the protruding portion 42 is configured to be larger than the outer diameter R _A1 of the protruding portion 48 so that they do not collide. Similarly, the outer diameter R _H1 of the protruding portion 43 is configured to be smaller than the inner diameter R _A2 of the protruding portion 47 so that they do not collide. By configuring in this positional relationship, the relative rotation angle between the hammer 41 and the anvil 46 can be configured to be greater than 180 degrees, and a sufficient amount of inversion angle of the hammer 41 can be secured with respect to the anvil 46. The reversal angle can be an acceleration zone before hitting the hammer 41 against the anvil 46.

Next, when the hammer 41 rotates forward to the state of FIG. 10 (3), the striking surface 42 a of the protruding portion 42 collides with the hit surface 47 a of the protruding portion 47. At the same time, the striking surface 43 a of the protrusion 43 collides with the striking surface 48 a of the protrusion 48. Thus, a well-balanced blow can be performed on the anvil 46 by colliding at two locations on the opposite side of the rotation axis. As a result of this impact, as shown in FIG. 10 (4), the anvil 46 rotates in the direction of the arrow 94, and the material to be fastened is tightened by this rotation. Incidentally, the hammer 41 is concentric position in the radial direction _{(R H2 above, R H3} following positions) has a collision detection section 42 is the only projection at concentric position _{(R H1} following positions) in the third with a collision detecting section 43 is the only projections. Further, the anvil 46 is concentric position in the radial direction _{(R A2} or _{higher, R A3} following positions) in having a collision detection section 47 is the only projection, the only projection in a concentric position _{(R A1} following positions) with a certain collision detection section 48.

  Next, a driving method of the impact tool 1 according to the present embodiment will be described. In the impact tool 1 according to the present embodiment, the anvil 46 and the hammer 41 are formed so as to be relatively rotatable at a rotation angle of less than 360 degrees. Accordingly, since the hammer 41 cannot rotate relative to the anvil 46 for more than one rotation, its rotation control is also unique. FIG. 11 is a diagram illustrating a trigger signal, an inverter circuit drive signal, a rotation speed of the motor 3, and a hammering state of the hammer 41 and the anvil 46 when the impact tool 1 is operated. In each graph, the horizontal axis is time, and the horizontal axis is shown together so that the timing of each graph can be compared.

In the impact tool 1 according to the present embodiment, in the case of tightening work in the impact mode, first fast tightening is performed in the continuous drive mode, and when the necessary tightening torque value becomes large, the pulse mode (1) is switched to perform tightening. When the necessary tightening torque value is further increased, the pulse mode (2) is switched to perform tightening. In the continuous drive mode in T ₂ from the time T ₁ of the FIG. 11, the arithmetic unit 51 performs control based on the motor 3 to the target speed. Therefore, the motor 3 accelerates the motor until the target rotational speed indicated by the arrow 85a is reached. Thereafter, when the tightening reaction force from the tip tool attached to the anvil 46 increases, the rotational speed of the motor 3 gradually decreases. Therefore, by detecting a current value supplied to the drop in the rotational speed of the motor 3 is switched to the rotation drive mode by the pulse mode (1) at time T _2.

The pulse mode (1) is a mode in which the motor 3 is driven intermittently rather than continuously, and is driven in a pulse shape so that “pause → forward rotation driving” is repeated a plurality of times. Here, “driving in a pulsed manner” means that the drive current supplied to the motor 3 is pulsated by pulsating the gate signal applied to the inverter circuit 52, thereby pulsating the rotation speed or output torque of the motor 3. It is to drive control so that. This pulsating the drive current OFF from time _{T 2} to _{T 21} is supplied to the motor (pause), the motor drive current ON from the time _{T 21} to _{T 3} (drive), from time _{T 3} to _{T 31} driven current OFF (pause), is generated by from time _{T 31} to time _{T 4} repeats ON-OFF of the drive current such that the driving current ON, a large period (e.g., several tens Hz~ hundred and several tens Hz) . Note that PWM control is performed to control the rotational speed of the motor 3 when the drive current is ON, but the pulsation cycle is sufficiently small compared to the duty ratio control cycle (usually several kilohertz).

In the example of FIG. 11, by resting the supply of the drive current from T ₂ to a certain time the motor 3, after the rotation speed of the motor 3 is decreased by an arrow 85b, calculating unit 51 (see FIG. 5) is the drive signal 83a Is sent to the control signal output circuit 53 to supply a pulsed drive current (drive pulse) to the motor 3 to accelerate the motor 3. This acceleration control does not necessarily mean driving at a duty ratio of 100%, but may be controlled at a duty ratio of less than 100%. Next, when the hammer 41 strongly collides with the anvil 46 at the point of the arrow 85c, a striking force is given as indicated by the arrow 88a. When the striking force is applied, the supply of the driving electric current to the motor 3 is again stopped for a predetermined period, and after the rotational speed of the motor has dropped as indicated by the arrow 85b, the calculation unit 51 sends the driving signal 83b to the control signal output circuit. The motor 3 is accelerated by sending it to 53. Then, the hammer 41 strongly collides with the anvil 46 at the point indicated by the arrow 85e, so that a striking force is given as indicated by the arrow 88b. In the pulse mode (1), the above-mentioned intermittent driving of the motor 3 that repeats “pause → forward rotation driving” is repeated once or a plurality of times. However, when a higher tightening torque is required, the state is detected. Then, the rotation mode is switched to the pulse mode (2). Whether or not a high tightening torque is required can be determined using, for example, the number of rotations of the motor 3 (before and after the arrow 85e) when the striking force indicated by the arrow 88b is applied.

  The pulse mode (2) is a mode in which the motor 3 is intermittently driven and the motor 3 is driven in a pulse shape as in the pulse mode (1), but “pause → reverse rotation drive → pause (stop) → normal “Rotation drive” is driven to repeat a plurality of times. That is, in the pulse mode (2), in order to apply not only forward rotation driving of the motor 3 but also reverse rotation driving, the hammer 41 is rotated forward by a sufficient relative angle with respect to the anvil 46, and then the hammer 41 is moved forward. It is accelerated in the direction of rotation and collides with the anvil 46 vigorously. By driving the hammer 41 in this way, a strong tightening torque is generated in the anvil 46.

When switched to the pulse mode (2) in T ₄ time example of FIG. 11, by pause the driving of the motor 3, the motor 3 by then sending a negative direction of the drive signal 84a to the control signal output circuit 53 Reverse rotation. Forward, when performing reverse rotation is achieved by switching the signal pattern of the drive signals (on-off signal) to be output from the control signal output circuit 53 to each of the switching elements Q1 to Q6. When the motor 3 rotates backward by a predetermined rotation angle, the driving of the motor 3 is temporarily stopped and the forward rotation driving is started. Therefore, the drive signal 84b in the positive direction is sent to the control signal output circuit 53. In the rotational drive using the inverter circuit 52, the drive signal is not switched to the plus side or the minus side. However, in FIG. It was expressed schematically by dividing it into two directions.

The hammer 41 collides with the anvil 46 in the vicinity where the rotational speed of the motor 3 reaches the maximum speed (arrow 86c). Due to this collision, a tightening torque 89a that is much larger than the tightening torque (88a, 88b) generated in the pulse mode (1) is generated. When the collision occurs in this way, the rotational speed of the motor 3 decreases so as to reach the arrows 86c to 86d. In addition, you may control to stop the drive signal to the motor 3 at the moment of detecting the collision shown by the arrow 89a. In that case, when the fastening target is a bolt or a nut, the reaction transmitted to the operator's hand after hitting. Is less. As shown in this embodiment, the reaction force to the worker is smaller than that in the continuous drive mode by causing the drive current to flow through the motor 3 even after a collision, which is suitable for work in an intermediate load state. In addition, the fastening speed is fast and the power consumption can be reduced as compared with the pulse strong mode. Then, Similarly, "pause → reverse rotation → pause (stop) → normal rotation driving" tight strong fastening torque by repeating a predetermined number of times is performed, releasing the operator trigger operation at time T ₇ As a result, the motor 3 stops and the tightening operation is completed. The completion of the work is determined not only by the release of the trigger operation by the operator, but also by the calculation unit 51 that the tightening with the set tightening torque is completed based on the output of the impact detection sensor 56 (see FIG. 5). Then, you may control so that the drive of the motor 3 may be stopped.

As described above, in this embodiment, the initial stage of tightening which requires less tightening torque is rotationally driven in the continuous drive mode, and as the tightening torque increases, tightening is performed in the pulse mode (1) with intermittent driving only in the forward direction. In the final stage of tightening, the tightening is performed strongly by the pulse mode (2) by intermittent driving by forward and reverse rotation of the motor 3. In addition, you may comprise so that it may drive using only pulse mode (1) and pulse mode (2). Further, it is possible to perform a control for directly shifting from the continuous drive mode to the pulse mode (2) without providing the pulse mode (1). In the pulse mode (2), the forward rotation and reverse rotation of the motor are alternately performed, so that the fastening speed is significantly slower than in the continuous drive mode and the pulse mode (1). When the tightening speed is suddenly decreased in this way, a sense of incongruity at the time of shifting to the striking operation becomes larger than that of an impact tool having a known rotary striking mechanism. Therefore, in transition from the continuous drive mode to the pulse mode (2), The feeling of operation becomes natural when the pulse mode (1) is interposed. Furthermore, the tightening operation time can be shortened by performing the tightening in the continuous drive mode or the pulse mode (1) as much as possible.

  Next, the control procedure of the impact tool 1 according to the present invention will be described with reference to FIGS. FIG. 12 is a flowchart showing a control procedure of the impact tool 1 according to the embodiment of the present invention. The impact tool 1 determines whether or not the impact mode has been selected using the toggle switch 32 (see FIG. 2) prior to the start of work by the worker (step 101). If the impact mode is selected, the process proceeds to step 102. If not selected, that is, if the normal drill mode is selected, the process proceeds to step 110.

In the impact mode, the calculation unit 51 determines whether or not the trigger switch 8 is turned on. If the trigger switch 8 is turned on (the trigger operation unit 8a is pulled), the motor is operated in the continuous drive mode as shown in FIG. 3 is started (step 103), and PWM control of the inverter circuit 52 is started according to the pulling amount of the trigger operation unit 8a (step 104). The rotation of the motor 3 is accelerated while controlling so that the peak current supplied to the motor 3 does not exceed the upper limit p. Next, the current value I supplied to the motor 3 after elapse of t milliseconds has been detected using the output of the current detection circuit 59 (see FIG. 5). The detected current value I returns to step 104 If not exceeded p1 amps, the flow proceeds to step 108 If exceeded (step 107). Next, it is determined whether or not the detected current value I exceeds p2 amperes (step 108).

  In step 108, if the detected current value I does not exceed p2 [A], that is, if the relationship of p1 <I <p2 is satisfied, the procedure of the pulse mode (1) shown in FIG. The process proceeds to 109 (step 120), and if the detected current value I exceeds p2 [A], the process proceeds directly to step 109 without executing the procedure of the pulse mode (1). In step 109, it is determined whether or not the trigger switch 8 is turned on. If the trigger switch 8 is turned off, the process returns to step 101. If the ON state continues, the procedure of the pulse mode (2) shown in FIG. 16 is executed. Then, the process returns to step 101.

  When the drill mode is selected in step 101, the drill mode 110 is executed, and the control is the same as the control in steps 102 to 107. Then, as p1 in step 107, the control mode in the electronic clutch or the overcurrent state immediately before the motor 3 is locked is detected and the motor 3 is stopped (step 111), thereby terminating the drill mode. Return.

Here, the procedure for determining the mode transition in steps 107 and 108 will be described with reference to FIG. The upper graph shows the relationship between the elapsed time and the number of revolutions of the motor 3, and the lower graph shows the relationship between the current value supplied to the motor 3 and time, and the time axes of the upper and lower graphs are the same. I have to. In the left graph, when the trigger switch is pulled at time T _A (corresponding to step 102 of FIG. 12), the motor 3 is accelerated is started as indicated by the arrow 113a. During this acceleration, constant current control is performed in a state where the maximum current value p is limited as indicated by an arrow 114a. When the rotation speed of the motor 3 reaches a predetermined rotation speed (arrow 113b), the current value decreases because the acceleration current is changed to the steady-state current as indicated by the arrow 114b. Thereafter, when the reaction force received from the fastening member increases as the fastening of screws, bolts, and the like proceeds, the rotational speed of the motor 3 gradually decreases as indicated by the arrow 113c, and the current supplied to the motor 3 The value increases. Then, the current value is determined after elapse of t milliseconds from the start of the motor 3, and as shown by an arrow 114c, when the relationship of p1 <I <p2 is satisfied, as shown in step 120, the pulse mode (1) described later is set. Transition to control.

In the right side of the graph, when the trigger switch is pulled at time T _B (corresponding to step 102 of FIG. 12), the motor 3 is accelerated is started as indicated by the arrow 115a. During this acceleration, constant current control is performed in a state where the maximum current value p is limited as indicated by an arrow 116a. When the rotation speed of the motor 3 reaches a predetermined rotation speed (arrow 115b), the current value decreases because the acceleration current is changed to the steady-state current as indicated by the arrow 116b. Thereafter, when the reaction force received from the fastening member increases as the fastening of screws, bolts, and the like proceeds, the rotational speed of the motor 3 gradually decreases as indicated by an arrow 115c, and the current supplied to the motor 3 The value increases. In this example, since the reaction force received from the fastening member has increased abruptly, as indicated by an arrow 116c, the rotational speed of the motor 3 is greatly reduced, and the current value is greatly increased. Since the current value after elapse of t milliseconds from the start of the motor 3 has a relationship of p2 <I as indicated by 116c, the control shifts to the control of the pulse mode (2) shown in FIG. To do.

Normally, when tightening screws and bolts, the required tightening torque may not be constant due to variations in the processing accuracy of screws and bolts, the condition of the material to be fastened, and variations in materials such as wood nodes and grain. Many. Therefore, it may be possible to perform tightening at a stretch until just before the tightening is completed only in the continuous drive mode. In such a case, the tightening operation can be completed efficiently in a short time by skipping the tightening in the pulse mode (1) and shifting to the tightening in the pulse mode (2) having a higher tightening torque.

Next, the control procedure of the impact tool in the pulse mode (1) will be described using the flowchart of FIG. When the mode is changed to the pulse mode (1), first, after a predetermined rest period, the peak current is limited to p3 amperes or less (step 121), and the forward current is applied to the motor 3 for a predetermined time, that is, T milliseconds. By supplying, the motor 3 is rotated (step 122). Next, after the elapse of time T milliseconds, the rotational speed N _1n (where n = 1, 2,...) [Rpm] of the motor 3 at that time is detected (step 123). Next, the drive current supplied to the motor 3 is turned off, and the time t _1n required to decelerate until the rotational speed of the motor 3 decreases from N _1n to N _2n (= N _1n / 2) is measured. _Next, determine the _{t 2n} from _t 2n = _{X-t 1n,} the forward current is added to only the motor 3 period of _{t 2n} (step 126), to accelerate the motor 3 while holding the peak current below p3 amps. _Then, when the rotation speed _{N 1} of the motor 3 after the lapse of _{t 2n} times _{(n + 1)} may determine whether the threshold rotation speed _{R th} hereinafter for shifting to the pulse mode _(2), is less than _{R th} is returning to step 120 of FIG. 12 ends the process of the pulse mode _(1), if it is _{R th} or returns to the step 124 (step 128).

FIG. 15 is a graph showing the relationship between the rotational speed of the motor 3 and the elapsed time during the execution of the procedure of the flowchart shown in FIG. 14, and the relationship between the current supplied to the motor 3 and the elapsed time. First, the drive current 132 is supplied to the motor 3 for a time T. Since the drive current is limited to a peak current of p3 ampere or less, the current during acceleration is limited as indicated by an arrow 132a, and then the current value decreases as indicated by an arrow 132b as the number of rotations of the motor 3 increases. At time _{T 1,} the rotation speed of the motor 3 when that reaches the _{N 11} is _measured, the rotational speed _{N 21} to start the rotation from the _N 21 ₌ N _11/2 of the motor 3 is calculated by calculation. Rotational speed _{N 11} is, for example, 10,000 rpm. When the rotation speed of the motor 3 is reduced to N _21, the driving current 133 is the motor 3 is supplied is accelerated again. The time t2n during which the drive current 133 is supplied is determined by t2n = X−t1n. Similarly, time 2X, performs the same control in 3X, tightening revolutions increase the degree of the motor 3 is decreased as the reaction force increases, it is the rotational speed N ₁₄ is equal to or less than the threshold rotational speed R _th at time 4X End up. At this time, the processing in the pulse mode (1) is completed, and the processing shifts to the processing in the pulse mode (2).

  Next, the control procedure of the impact tool in the pulse mode (2) will be described using the flowchart of FIG. First, the drive current supplied to the motor 3 is turned off and the system waits for 5 milliseconds (step 141). Next, a reverse current is supplied to the motor 3 so as to rotate the motor at −3000 rpm (step 142). Here, “minus” means to rotate at 3000 rpm in the direction opposite to the rotating direction during work. Next, when the rotation speed of the motor 3 reaches −3000 rpm, the current supplied to the motor 3 is turned off and the system waits for 5 milliseconds (step 143). The reason for waiting for 5 milliseconds here is that if the motor 3 is suddenly reversed in the reverse direction, the impact tool body may be shaken. In addition, it is possible to achieve energy saving because there is no power consumption during this standby time. Next, in order to rotate the motor 3 in the forward rotation direction, the forward rotation current is turned on (step 144). The current supplied to the motor 3 is turned off 95 milliseconds after the forward current is turned on, but the hammer 41 collides (hits) the anvil 46 before turning off this current, so A strong tightening torque is generated (step 145). Thereafter, it is detected whether the ON state of the trigger switch is maintained. If the trigger switch is OFF, the rotation of the motor 3 is stopped, the processing of the pulse mode (2) is terminated, and the process returns to step 140 in FIG. 147, 148). If it is determined in step 147 that the trigger switch 8 is on, the process returns to step 141 (step 147).

  As described above, according to the present embodiment, using a hammer and anvil having a relative rotation angle of less than one rotation, the motor is continuously rotated, intermittent rotation only in the positive direction, and intermittent rotation in the forward direction and the reverse direction. Thus, the fastening member can be fastened efficiently. Moreover, since the shape of the hammer and the anvil can be made simple, the impact tool can be reduced in size and cost can be reduced.

  As mentioned above, although demonstrated based on the Example which shows this invention, this invention is not limited to the above-mentioned Example, A various change is possible within the range which does not deviate from the meaning. For example, in the present embodiment, an example in which a brushless DC motor is used as the motor has been described. However, the present invention is not limited to this, and other types of motors that can be driven in the forward direction and the reverse direction may be used.

  In addition, the anvil and the hammer can have any shape, the anvil and the hammer cannot be relatively continuously rotated (cannot be rotated while riding over), ensure a predetermined rotation angle of less than 360 degrees, What is necessary is just to form a to-be-struck surface. For example, you may comprise so that the protrusion part of a hammer and an anvil may protrude not in the axial direction but in the circumferential direction. Further, the protrusions of the hammer and the anvil are not necessarily limited to the protrusions that protrude outward, and it is sufficient that the striking surface and the striking surface can be formed in any shape. (That is, a recess). Further, the striking surface and the striking surface are not necessarily limited to a flat surface, but may be a curved surface as long as it has a shape that can be hit and striked well.

1 Impact tool 3 Motor 3a (Motor) rotor 3b (Motor) stator
3c (Motor) Permanent Magnet 3d Insulating Member 3e (Motor) Coil 5 Case 6 Housing 6a (Housing) Body 6b (Housing) Grip 6c (Housing) Battery Holding Unit 7 Substrate 8 Trigger Switch 8a Trigger Operation Part 9 Control circuit board 10 Switching element 11 Cover 12 LED light 14 Forward / reverse switching lever 15 Sleeve 15a Spring 15b Washer 15c Retaining ring 16a Metal bearing 16b Bearing 17a, 17b Bearing 18 Cooling fan
18a Through hole 18b (for cooling fan) Cylindrical portion 18c (for cooling fan) Fin 18d (for cooling fan) Opening 19 (for motor) Rotating shaft 20 Screw boss 21 Planetary gear reduction mechanism 21a Sun gear 21b Planetary Gear 21c Rotating shaft 21d Outer gear 22 Inner cover 23 O-ring 24 Ball
26a, 26b Air intake port 26c Slit 30 Battery pack 30 a Release button 31 Control panel 32 Toggle switch ( impact mode / drill mode switch)
33 belt hook 34 strap
40 hammering mechanism 41 hammer 46 anvil 50 control unit 51 arithmetic unit 52 inverter circuit 53 control signal output circuit 54 rotor position detection circuit 55 rotation speed detection circuit 56 impact detection sensor 57 impact detection circuit 59 current detection circuit
60 Switch operation detection circuit 61 Applied voltage setting circuit 62 Rotation direction setting circuit 151 Hammer 151a Fitting shaft 151b Body portion 151c Disk portion 151d Connection portion 151f Through hole 152 Protruding portion 152a, 152b Stroke surface 153 Protruding portion 156 Anvil 156a Mounting hole 156b Main body portion 157 Protruding portion 157a, 157b Impact surface 158 Protruding portion

Claims (8)

A motor, a speed reduction mechanism for reducing the rotational force of the motor, a hammer connected to the output portion of the speed reduction mechanism and capable of continuous rotation, and a rotational force or a striking force provided by the hammer disposed on the front side of the hammer. Having an anvil that rotates a given tip tool;
An output tool of the speed reduction mechanism, the hammer, and the center axis of the anvil are impact tools arranged coaxially with the rotation axis of the motor ,
The hammer has a fitting portion formed on one or more sets of projection and the central axis projecting from the body portion in the radial outer side or axially,
Said anvil includes a pair or more protrusions projecting from the body portion radially outward or axially, a fitting portion for fitting portion and fitting of the hammer portions,
At least one protrusion of the anvil and the hammer has a striking surface that collides with each other,
The impact tool, wherein the anvil and the hammer are formed so that the protrusions of the anvil and the hammer can rotate relative to each other at a maximum rotation angle of 60 degrees or more and less than 360 degrees. The speed reduction mechanism is a planetary gear mechanism, a rotation shaft of the motor is connected to a sun gear of the planetary gear mechanism, and the hammer is fixed so as to connect rotation shafts of a plurality of planetary gears of the planetary gear mechanism. The impact tool according to claim 1. The impact tool according to claim 1, wherein the hammer and the anvil are each made of an integral metal structure. By rotating the motor in the forward and reverse impact tool according to claim 3, wherein the intermittent blow to Rukoto the hammer against the anvil. The hammer and the anvil are provided with two blade portions extending radially outward from the main body portion,
The impact tool according to claim 4, wherein the protruding portion is formed on the blade portion. Each of the blade portions is formed with two projecting portions having striking surfaces, and the plurality of striking surfaces formed on the hammer projecting portions collide simultaneously with the plurality of striking surfaces formed on the projecting portions of the anvil. The impact tool according to claim 5, wherein the impact tool is configured to do so.   The impact tool according to any one of claims 1 to 6, wherein the anvil and the hammer hitting portion rotate relatively at a maximum rotation angle of 180 degrees or more and less than 360 degrees. Possess a motor, a reduction mechanism for reducing the rotational force of the motor, and the hammer which is capable of continuous rotation are directly connected to the output of the speed reduction mechanism, an anvil is struck in the rotational direction by the hammer,
The central axis of the anvil output portion and the hammer of the reduction mechanism, an impact tool which Ru is disposed coaxially with the rotary axis of the motor,
The hammer has one or more sets of projecting portions projecting radially outward or axially from the main body portion and a fitting portion formed on the central axis, and is fixed so as not to move in the axial direction with respect to the anvil. ,
The anvil has a protruding portion that protrudes radially outward or axially from the main body portion, and a fitting portion that fits with a fitting portion of the hammer portion,
At least one protrusion of the anvil and the hammer has a striking surface that collides with each other,
The hammer can be rotated at a maximum rotation angle of less than 360 degrees relative to the anvil , and the hammer can be rotated 180 degrees or more with respect to the anvil as a run-up rotation before hitting. Characteristic impact tool.

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