JP2006123080A - Impact tool - Google Patents

Impact tool Download PDF

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Publication number
JP2006123080A
JP2006123080A JP2004314598A JP2004314598A JP2006123080A JP 2006123080 A JP2006123080 A JP 2006123080A JP 2004314598 A JP2004314598 A JP 2004314598A JP 2004314598 A JP2004314598 A JP 2004314598A JP 2006123080 A JP2006123080 A JP 2006123080A
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Japan
Prior art keywords
switching
vibration
impact
mechanism
switching member
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JP2004314598A
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JP4468786B2 (en
Inventor
Takefumi Furuta
岳文 古田
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Makita Corp
株式会社マキタ
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Priority to JP2004314598A priority Critical patent/JP4468786B2/en
Priority claimed from US11/251,987 external-priority patent/US7308948B2/en
Publication of JP2006123080A publication Critical patent/JP2006123080A/en
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Publication of JP4468786B2 publication Critical patent/JP4468786B2/en
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Abstract

PROBLEM TO BE SOLVED: To select an operation mode with good operability without fear of erroneous operation even if there are many operation modes.
SOLUTION: A gear case 12 in a housing is provided with a clutch switching groove 65 in which an operation projection 62 of a clutch switching lever 57 is engaged, and a stepped pin 83 that passes through an impact switching groove 84 and engages with an auxiliary ring 78. Each of the switching positions of the respective switching members according to the rotational position integral with the switching plate 31. The slit 81 for guiding the guide body 82 and the vibration switching groove 101 with which the operation projection 98 of the vibration switching lever 93 is engaged. The changeover case 64 that can be changed is externally mounted, and the changeover plate 31 and the changeover case 64 are rotated from the outside of the housing by the changeover button 30 so that only one changeover button 30 is operated, and the drill mode and the impact mode All the operation modes, the vibration drill mode and the clutch mode, can be selected.
[Selection] Figure 7

Description

  The present invention relates to an impact tool such as an impact driver provided with a striking mechanism capable of imparting intermittent striking in a rotational direction to an output shaft protruding forward in the housing.

  As an impact tool, for example, a tool described in Patent Document 1 is known. Here, the rotation of the output shaft of the motor is transmitted to the drive shaft in the housing via the planetary gear reduction mechanism, and a hammer that is biased forward by a coil spring is externally attached to the drive shaft via a ball, The rotation of the drive shaft is transmitted to the anvil via the hammer by engaging the hammer with an arm of an anvil (output shaft) protruding forward of the main body housing. When the load on the anvil increases, the hammer moves backward due to the rolling of the ball, temporarily disengages from the arm of the anvil, and reengages with the arm while moving forward again by the bias of the coil spring. This hammer action causes intermittent hits on the anvil (impact mode).

  And here, it is possible to select a drill mode in which the hitting by the hitting mechanism is canceled and no hit is generated on the anvil. The release means is provided so that the final stage carrier of the planetary gear speed reduction mechanism can be moved in the axial direction and can be moved from the outside by an operating member, and the carrier is connected to the carrier via a switching pin passing through the axis of the drive shaft. The connecting member as a switching member that can be engaged with both the drive shaft and the anvil is connected, and the connecting member is moved to a slide position that engages with both the drive shaft and the anvil by moving the carrier by the operation member. By doing so, the drive shaft and the anvil are integrated.

JP 2000-317854 A

By the way, in the impact tool, in addition to the impact mode and the drill mode, there is a case where a clutch mode (driver mode) is provided that can interrupt rotation transmission with a predetermined torque to the anvil. For example, this structure enables rotation of one of the internal gears of the planetary gear reduction mechanism provided between the motor and the output shaft, and the internal gear is engaged with a ball engaged with the end face of the internal gear. It is obtained by providing pressing means for pressing with a coil spring through a washer or the like. That is, when the load on the anvil increases and exceeds the urging force of the coil spring, the internal gear is idled and the rotation transmission to the anvil is interrupted.
On the other hand, in addition to the impact mode and the drill mode, a vibration drill mode for generating a vibration in the axial direction on the anvil may be provided. For example, this structure allows the anvil to move slightly in the front-rear direction and normally urges the anvil to the forward position. At the retracted position of the anvil, the anvil vibrates due to the engagement between the cams provided in the anvil and the housing. It is something to be made.

  Therefore, when the clutch mode or the vibration drill mode is applied, a switching mechanism between the drill mode is further required. For example, in the clutch mode, the switching member that can be engaged with the internal gear is slid between the engagement position with the internal gear and the non-engagement position by rotating the operation member such as a change ring. In addition, a structure for selecting the internal gear rotation restriction and its release is employed. Further, in the vibration drill mode, one of the cams is fixed to the anvil, the other cam is rotatable in the housing, and the switching member that can be engaged with the other cam is moved from the engagement position to the cam by the operating member. The structure etc. which select the provision and the cancellation | release of a vibration by sliding between non-engagement positions are employ | adopted.

  When the number of operation modes that can be selected increases, it is necessary to separately operate the impact switching member that switches between the impact mode and the drill mode, and the clutch switching member and the vibration switching member that switch the drill mode between the clutch mode and the vibration drill mode. In addition, the operability is deteriorated and there is a risk of erroneous operation.

  SUMMARY OF THE INVENTION Accordingly, it is an object of the present invention to provide an impact tool capable of selecting an operation mode with good operability without fear of erroneous operation even when there are many operation modes. .

In order to achieve the above object, an invention according to claim 1 is an impact tool having a clutch mechanism, which is engaged simultaneously with a clutch switching member and an impact switching member in a housing and moved to a predetermined position. By providing a common switching member that can change the combination of the slide positions by moving both switching members, and by operating the common switching member to move from the outside of the housing, the impact imparting by the striking mechanism and the internal gear rotation restriction can be achieved. Impact mode that performs the same operation, clutch mode that simultaneously releases the impact imparted by the impact mechanism and release of the internal gear rotation restriction, and drill mode that simultaneously releases the impact impartment by the impact mechanism and the internal gear rotation restriction And are selectable respectively.
In addition to the object of claim 1, the invention described in claim 2 can impart a vibration in the axial direction to the output shaft in the housing in order to obtain a good usability even in a case where a vibration mechanism is provided. For those equipped with a vibration mechanism and a second release means that can release the vibration to the output shaft by the vibration mechanism, the second release means is operated to release the vibration from the vibration mechanism. A third switching member that is slidable between the first slide position to be moved and the second slide position to which vibration is imparted by the vibration mechanism without operating the second release means, and this is a common switching member And the sliding position of the third switching member is combined by moving the common switching member, so that the impact imparting by the striking mechanism is released, the internal gear rotation is restricted, and the vibration is imparted by the vibration mechanism at the same time. Vibration drill mode is also one in which was further can be selected.

In order to achieve the above object, an invention according to claim 3 is an impact tool having a vibration mechanism, wherein the impact tool is engaged with the impact switching member and the vibration switching member simultaneously in the housing, and moved to a predetermined position. By providing a common switching member that can change the combination of each slide position by moving both switching members and moving the common switching member from the outside of the housing, the impact imparting by the striking mechanism and the vibration imparting by the vibration mechanism are released. Drill mode that simultaneously releases impact applied by the striking mechanism and release of vibration imparted by the vibration mechanism, and a vibration drill that simultaneously releases the shock imparted by the striking mechanism and imparts vibration by the vibration mechanism Each mode can be selected.
In addition to the object of any one of claims 1 to 3, the invention described in claim 4 includes another planetary gear reduction mechanism in order to facilitate speed switching and further improve usability. In the case of providing a speed switching member that is slidable between a coupling position where the null gear is coupled with any of the carriers before and after the null gear and a coupling release position where the coupling between the internal gear and the carrier is released, By engaging the speed switching member with the common switching member and combining the slide positions of the speed switching member by moving the common switching member, speed switching in an arbitrary mode is possible.
According to a fifth aspect of the present invention, in addition to the object of any one of the first to fourth aspects, the common switching member is provided with a planetary gear speed reduction so that each switching member can be slid by the common switching member without difficulty. Formed on the outer periphery of the gear case that houses the mechanism and the striking mechanism, and formed by a switching case that moves by the operation of the switching button exposed to the outside of the housing. One direction restriction groove provided on one side, provided on the other side, a switching groove having a direction different from that of the restriction groove, the restriction groove and the switching groove, and provided on either the switching case or the switching member, The switching member is slid along the restricting groove by the guide of the switching groove accompanying the movement of the switching case, and is configured to be performed respectively.

According to invention of Claim 1 and 3, all the operation modes can be selected only by operation of a common switching member. Therefore, there is no fear of erroneous operation, and operability and reliability are excellent.
According to the second aspect of the invention, in addition to the effect of the first aspect, even if the vibration drill mode is increased, the operability is not changed, and good usability can be maintained.
According to the fourth aspect of the present invention, in addition to the effect of any one of the first to third aspects, speed switching can be performed simultaneously by the common switching member, and further improvement in usability can be expected.
According to the fifth aspect of the present invention, in addition to the effect of any one of the first to fourth aspects, each switching member can be reliably guided to the slide position without difficulty.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
FIG. 1 is a longitudinal sectional view showing an impact driver which is an example of an impact tool. The impact driver 1 is located at a rear portion (a right side in FIG. 1 is a front side) of a main body housing 2 including a pair of left and right halved housings. A planetary gear reduction mechanism 5, a striking mechanism 6, and a vibration mechanism 7 having a clutch mechanism are provided in the front of the motor 3, and an anvil 8 coaxial with the motor shaft 4 of the motor 3 is housed therein. Projecting forward. 9 is a switch of the drive circuit of the motor 3, and 10 is a trigger for turning on the switch 9 by pushing operation.
As shown in FIGS. 2 and 3, the planetary gear reduction mechanism 5 is coupled to the front of the motor bracket 11 and a cylindrical motor bracket 11 that is fixed in the main body housing 2 and supports the motor shaft 4. It is housed inside a cylindrical gear case 12 that is one size larger. That is, the three planetary gears 14, 14... Meshed with the pinion fitted to the motor shaft 4 and rotatable within the first internal gear 13, the carrier 15 that supports the planetary gear 14, and the carrier 15 , And the next planetary gears 17, 17... That can rotate within the second internal gear 16, and a carrier portion 19 that supports the planetary gear 17. 8 is formed from a spindle 18 that is coaxially inserted on the rear surface of the motor 8, and the rotation of the motor shaft 4 is decelerated in two stages so as to be transmitted to the spindle 18.

  Here, the first internal gear 13 is rotatably supported by a ball bearing 20 in the motor bracket 11, and a speed switching ring (speed switching member) 21 that holds the ball bearing 20 is shown in FIG. As shown also in B), the three protrusions 22, 22... Projecting in the axial direction on the outer surface, and the two guide grooves 23, 23 and 1 recessed corresponding to the inside of the motor bracket 11. By fitting with the two slits 24, it is possible to move back and forth in the axial direction in a state where rotation is restricted. Of the three ridges 22 of the speed switching ring 21, the ridge 22 fitted into the slit 24 is provided with a connecting piece 25 projecting in the radial direction, and a rectangular frame provided outside the motor bracket 11. 26 is loosely inserted. The frame 26 is externally mounted on the motor bracket 11 and is provided so as to be movable back and forth between a forward position where it contacts the rear end of the gear case 12 and a backward position where it contacts a step provided on the inner surface of the main body housing 2. It is connected to the ring-shaped speed switching lever 27 in an orthogonal shape, and a groove 28 is formed on the outer periphery of the speed switching lever 27 in the circumferential direction except for the frame 26 portion. Further, in the frame 26, coil springs 29, 29 are inserted in the front and rear sides so as to sandwich the connecting piece 25.

  On the other hand, on the outer periphery of the gear case 12, an arc-shaped switching plate 31 having a switching button 30 protruding on the upper surface is provided. As shown in FIG. 4, the switching plate 31 exposes the switching button 30 to the outside through a horizontally long rectangular window 32 drilled in the left-right direction on the upper surface of the main body housing 2. Is movable in the circumferential direction of the gear case 12 within a range in which movement is restricted within the window 32. However, since a retreating portion 33 to which the switching button 30 can retreat is connected to the left end of the window 32, if the switching button 30 is slid into the retreating portion 33 at the left end, the switching plate 31 is moved backward. Can be moved. In addition, a rectangular and thin protective plate 34 that exposes only the switching button 30 is set on the upper surface of the switching plate 31, and always covers the entire surface of the window 32 regardless of the sliding position of the front, rear, left, and right of the switching button 30. To prevent intrusion of dust.

  On the inner surface of the switching plate 31, a coupling protrusion 35 that is inserted into the concave groove 28 of the speed switching lever 27 protrudes so that the speed switching lever 27 can follow the movement of the switching plate 31 in the front-rear direction. . Similarly, between the main body housing 2 and the protection plate 34, bent pieces 37, 37 formed downward on the left and right sides of the rear end are formed as a pair of flat L-shaped stoppers formed on the upper rear surface of the speed switching lever 27. A flat U-shaped display plate 36 which is locked on the outer side of each of the pieces 38 and 38 is set, and the switching button 30 can be fitted at the left end position of the window 32. The display plate 36 contributes to the connection between the speed switching lever 27 and the switching plate 31, and the display pieces 39, 39 positioned before and after the switching button 30 are placed in the window 32 according to the front and rear positions of the switching button 30. The numbers displayed on the surface are visible by alternately exposing them.

  Accordingly, when the switching button 30 is operated at the left end position of the window 32 to move the switching plate 31 back and forth, the speed switching ring 21 and the first internal gear 13 follow and move back and forth via the speed switching lever 27. Will do. Here, at the forward position of the speed switching ring 21 and the first internal gear 13, the first stage planetary gear 14 and the carrier 15 are simultaneously meshed and coupled to each other, and at the reverse position, only the planetary gear 14 is meshed. Then, the coupling with the carrier 15 is released. On the outer periphery of the rear end of the first internal gear 13, meshing teeth 40, 40... Project at equal intervals in the circumferential direction, and project on the bottom surface of the motor bracket 11 at the retracted position of the first internal gear 13. It engages with the provided meshing teeth 41, 41,... To restrict the rotation of the first internal gear 13. Therefore, at the retracted position of the first internal gear 13, the rotation of the motor shaft 4 of the motor 3 is transmitted to the carrier 15 by being decelerated by the planetary gear 14 revolving in the first internal gear 13, and the planetary gear reduction mechanism 5. Thus, the low-speed mode is reduced in two stages, and at the forward position of the first internal gear 13, the high-speed mode in which the rotation of the motor shaft 4 is directly transmitted to the carrier 15 is set.

  At this time, the display plate 36 exposes the rear display piece 39 in the retracted portion 33 of the window 32 at the forward position of the switching button 30 to display the number “2” indicating that it is in the high speed mode. At the retracted position of 30, the front display piece 39 is exposed in the window 32 and the number “1” indicating the low speed mode is displayed. Further, when the first internal gear 13 slides and meshes with the carrier 15 and the meshing teeth 41, even if the positions of the teeth are not aligned, the speed switching lever 27 is elastic of the coil springs 29 and 29. Since it can move to an appropriate position by deformation, the switching operation itself can always be performed smoothly. Since the urging by the coil springs 29 and 29 continues as it is, the first internal gear 13 and the speed switching ring 21 slide to the proper front and rear positions at the proper meshing position when the motor shaft 4 rotates.

  The second internal gear 16 is also provided so as to be able to rotate within the gear case 12 while holding a ball bearing 42 that pivotally supports the carrier portion 19 of the spindle 18, and the front and rear surfaces in the circumferential direction are inclined surfaces. Engaging projections 43, 43,... Are projected at equal intervals in the circumferential direction. In front of the second internal gear 16, a pressing ring 44 is fitted by an axial protrusion 45, 45... Formed on the outer surface of the pressing ring 44 and a not-shown concave groove formed in the inner surface of the gear case 12. Engagement projections 46 of the same shape that can be engaged with the engagement projections 43, 43,... Are accommodated on the rear surface facing the second internal gear 16 so as to be movable in the axial direction while being restricted in rotation. 46 are projected at equal intervals in the circumferential direction. On the other hand, a coil spring 50 whose front end is received by a pair of pushers 47, 47 is disposed in front of the pressing ring 44 so that the pressing ring 44 can be urged rearward. The pushers 47, 47 are provided on the outer surface of the gear case 12 in a point-symmetrical manner around the shaft center, and stopper pieces 48, 48 protruding from the inner surface are passed through openings 51, 51 formed in the gear case 12. The stopper pieces 48 and 48 receive the front end of the coil spring 50 through the washer 52 by a plate-like body protruding inward. Male screw portions 49 are formed on the outer surfaces of the pushers 47, 47, respectively.

  Therefore, the second internal gear 16 is pressed and fixed by the coil spring 50 and the pressing ring 44 serving as pressing means, and the rotation is restricted. A cylindrical change ring 53 having a female screw part formed on the inner periphery is rotatably mounted on the gear case 12 in front of the main body housing 2 and screwed with the male screw part 49 of the pushers 47 and 47. When the pushers 47 and 47 are moved in the axial direction by rotating the change ring 53, the coil spring 50 can be expanded and contracted in the axial direction to change the urging force to the pressing ring 44. A leaf spring 54 is fitted on the outer periphery of the front end of the gear case 12 and engaged with teeth 55, 55... Formed on the inner periphery of the front end of the change ring 53. It has come to be obtained. A hammer case 56 is fixed to the gear case 12 with screws in front of the change ring 53 and pivotally supports the anvil 8, and forms the housing of the present invention together with the main body housing 2 and the change ring 53. A ring-shaped rubber bumper 114 is fitted to the front portion of the hammer case 53 to prevent damage to the workpiece due to the contact of the front portion of the impact driver 1 together with the screws.

  On the other hand, on the outer periphery of the second internal gear 16, as shown in FIG. 6 (A), the protrusions 58, 58.. A ring-shaped clutch switching lever (clutch switching member) 57 whose rotation is restricted by fitting with the recessed grooves 59, 59,... The engaging teeth 60, 60... Provided on the inner periphery thereof engage with the engaging teeth 61, 61... Provided on the rear outer periphery of the second internal gear 16. Regardless, the rotation of the second internal gear 16 can be restricted. On the outer surface of the clutch switching lever 57, a pair of connecting projections 62, 62 serving as a connecting body project from the point of symmetry in the radial direction and are slits 63, 63 as restriction grooves formed in the axial direction on the gear case 12. And protrudes to the outside of the gear case 12.

  A semi-cylindrical switching case 64 that is slightly larger than the gear case 12 is rotatably mounted on the outer periphery of the gear case 12. The switching case 64 is configured such that the switching plate 31 is fitted in the notch portion at the rear end and rotates integrally following the sliding in the circumferential direction of the switching plate 31. Form. A pair of clutch switching grooves 65, 65 are formed at a point symmetrical position at the rear end portion of the switching case 64, and the coupling protrusions 62 of the clutch switching lever 57 are inserted into the clutch switching grooves 65, 65, respectively. As shown in FIG. 5A, each clutch switching groove 65 includes a first groove 66 along the circumferential direction of the switching case 64 and a second circumferentially located second position located behind the first groove 66. The connecting protrusion 62 is formed of a groove 67 and an inclined groove 68 that connects the first groove 66 and the second groove 67 and is restricted from moving in the circumferential direction by the slit 63 as the switching case 64 rotates. By relatively moving in the clutch switching groove 65, the clutch switching lever 57 can be moved back and forth from the outside via the connection protrusion 62. Here, the forward position (first slide position) of the clutch switching lever 57 when the connection protrusion 62 is positioned in the first groove 66, and the backward position (second position) of the clutch switching lever 57 when it is positioned in the second groove 67. Slide position).

  The striking mechanism 6 includes an anvil 8 that is pivotally supported via ball bearings 69 and 69 on a small cylindrical portion 12 a and a hammer case 56 provided at the front end of the gear case 12, and a spindle 18 that is coaxially inserted into the rear surface of the anvil 8. And a hammer 70 mounted on the spindle 18, and a coil spring 72 that receives the rear end by a cup washer 71 mounted on the spindle 18 and biases the hammer 70 forward. As shown in FIG. 6B, the hammer 70 is formed in a pair of cam grooves 73 and 73 formed in a V shape on the outer peripheral surface of the spindle 18 and in the axial direction on the inner peripheral surface of the hammer 70. The steel ball 75 is connected to the spindle 18 by two steel balls 75, 75 fitted across the connection grooves 74, 74, and the steel ball 75 is connected to the front end (V-shaped tip) of the cam groove 73 and the connection by the coil spring 72. The groove 74 is biased to the forward position located at the rear end. On the front surface of the hammer 70, a pair of fan-like engagement claws 77, 77 projecting from the front that can be engaged with a pair of arms 76, 76 extending radially to the rear end of the anvil 8 are projected. In the forward position of the hammer 70 shown in FIG. 1, the engaging claws 77 and 77 engage with the arms 76 and 76 to rotate the hammer 70 and the anvil 8 together.

  An auxiliary ring 78 serving as a releasing means of the striking mechanism 6 is externally mounted on the hammer 70 so as to rotate integrally with the hammer 70 and move independently in the axial direction. On the front surface of the auxiliary ring 78, arc-shaped auxiliary claws 79, 79 continuously projecting from the outer peripheries of the engaging claws 77, 77 of the hammer 70 are projected, and the engaging claws 77 of the hammer 70 are in the forward position. , 77 and the arms 76, 76. Further, a concave groove 80 is formed in the circumferential direction on the outer periphery of the auxiliary ring 78. On the other hand, the switching case 64 has rectangular guide bodies (impact switching members) 82 and 82 in which a cylindrical body 82a is fitted in the center in a pair of slits (regulating grooves) 81 and 81 formed in the axial direction. As shown in FIGS. 5A and 6B, a stepped pin (connecting body) 83 that is accommodated so as to be movable back and forth and is fitted into the cylindrical body 82a of each guide body 82 is formed in the gear case 12. The tip is loosely inserted into the concave groove 80 of the auxiliary ring 78 through the pair of impact switching grooves 84, 84.

  The impact switching groove 84 is formed of a first groove 85 formed in the circumferential direction of the gear case 12 and a second groove 86 bent in a V shape rearward in the middle of the first groove 85. With the rotation of 64, the stepped pins 83 and 83 are moved in the impact switching grooves 84 and 84 together with the guide bodies 82 and 82 that are restricted from moving in the circumferential direction in the slit 81, whereby the stepped pin 83 is moved. The auxiliary ring 78 can be moved back and forth from the outside. Here, the stepped pin 83 is located at the advance position (first slide position) of the guide body 82 located in the first groove 85, the advance position of the auxiliary ring 78, and the guide located at the V-shaped tip of the second groove 86. The retracted position of the auxiliary ring 78 is obtained at the retracted position of the body 82 (second slide position). In the impact switching groove 84, a cylindrical body 82a of a suitable guide body 82 that is externally mounted on the stepped pin 83 slides. Such a double structure with the cylindrical body 82a and the stepped pin 83 ensures the strength of the stepped pin 83, allows the stepped pin 83 to slide within the impact switching groove 84 and the auxiliary ring 78. This is for the purpose of reliably moving.

  The vibration mechanism 7 is installed in the hammer case 56. The vibration mechanism 7 includes a first cam 87 that is integrally fitted to the anvil 8 between the ball bearings 69, 69, and a separate exterior to the anvil 8 behind the ball 88, 88, and a flat washer 89. The second cam 90 whose rearward movement is restricted by the second cam 90, and the locking teeth 91, 91 formed on the outer periphery of the second cam 90 in the small cylinder portion 12a of the gear case 12 behind the second cam 90. .. A ring-shaped vibration switching lever (vibration switching member) 93 having engaging teeth 92, 92... That can mesh with each other, and the first cam 87 and the second cam 90 facing each other. Are formed with cam teeth 94, 95,. The second cam 90 and the vibration switching lever 93 serve as releasing means for the vibration mechanism 7.

As shown in FIG. 6C, the vibration switching lever 93 is formed by fitting projections 96, 96,... Projecting on the outer periphery and recesses 97, 97,. A pair of connecting protrusions (connectors) 98, 98 that are held so as to be able to move back and forth in the small tube portion 12a in a state where the rotation is restricted and project radially outwardly between the protrusions 96, 96 The slits (regulating grooves) 99 and 99 provided in 12 a are passed through and loosely inserted into a pair of arcuate guide plates 100 and 100 protruding from the front end of the switching case 64. As shown in FIG. 7, a first groove 102 along the circumferential direction of the switching case 64 and a trapezoidal shape forward in the middle of the first groove 102 are formed in the loose insertion portion of the connection protrusion 98 in each guide plate 100. The vibration switching groove 101 formed by the second groove 103 that is bent in the direction is formed, and the connection protrusions 98, 98 that are restricted from moving in the circumferential direction in the slit 99 as the switching case 64 rotates are connected to the vibration switching groove 101. By moving relatively within 101, 101, the vibration switching lever 93 can be moved back and forth from the outside via the connecting projection 98. Here, when the connection protrusion 98 is located in the first groove 102, the vibration switching lever 93 moves backward (first slide position), and when the connection protrusion 98 is located at the trapezoidal front end of the second groove 103, the vibration switching lever 93 moves forward. A position (second slide position) is obtained.
Here, since the switching case 64 is made of synthetic resin, the portions including the rear edge of the second groove 103 in the guide plate 100 are formed separately by the steel plates 104 and 104, respectively, and the vibration switching groove 101 is formed. The strength of is secured.

Next, the rotation position of the switching case 64 associated with the operation of the switching button 30 and the operation mode obtained along with the rotation position will be described.
First, as shown in FIG. 7, the switching button 30 is at the first rotation position of the switching case 64, which is the first position of the left end of the window 32 (upper side in FIG. 4. In the clutch switching groove 65, the coupling protrusion 62 of the clutch switching lever 57 is positioned at the right end of the first groove 66. Therefore, the clutch switching lever 57 is in the forward position and restricts the rotation of the second internal gear 16. In the impact switching groove 84, the stepped pin 83 is positioned at the left end of the first groove 85. Therefore, the auxiliary ring 78 is in the forward movement position and is engaged with the arm 76. Further, in the vibration switching groove 101, the connection protrusion 98 is positioned at the right end of the first groove 102. Therefore, the vibration switching lever 93 is in the retracted position and is away from the second cam 90.
Therefore, here, the second internal gear 16 is directly prevented from idling by the clutch switching lever 57, and the anvil 8 is in a drill mode in which it rotates integrally with the spindle 18 via the auxiliary ring 78. At this time, since the second cam 90 is free to rotate, vibration does not occur even if it makes contact with the first cam 87.

Next, as shown in FIG. 8, at the second rotational position of the switching case 64 where the switching button 30 moves from the first position to the right side by about one third of the horizontal dimension of the window 32, the clutch switching groove 65 and In the vibration switching groove 101, the connecting protrusions 62 and 98 are not changed in the first grooves 66 and 102, respectively, so that the forward movement position of the clutch switching lever 57 and the backward movement position of the vibration switching lever 93 are not changed. However, in the impact switching groove 84, the stepped pin 83 enters the second groove 86 and moves to the V-shaped tip. Therefore, the auxiliary ring 78 moves backward from the arm 76.
Therefore, in the second position of the switching button 30, the second internal gear 16 is prevented from idling regardless of the load on the anvil 8, and the second cam 90 is also free to rotate and no vibration is generated. 8 is an impact mode connected via a hammer 70.

Next, as shown in FIG. 9, at the third rotational position of the switching case 64 where the switching button 30 moves from the second position to the right side by about one third of the horizontal dimension of the window 32, the clutch switching groove In 65, the connecting projection 62 remains unchanged in the first groove 66. However, in the impact switching groove 84, the stepped pin 83 enters the first groove 85 again, and moves the auxiliary ring 78 to the advanced position. Further, in the vibration switching groove 101, the connecting protrusion 98 enters the second groove 103 and moves to the trapezoidal front end. Therefore, the vibration switching lever 93 moves forward and restricts the rotation of the second cam 90.
Accordingly, at the third position of the switching button 30, the second internal gear 16 is prevented from idling regardless of the load on the anvil 8, and the anvil 8 rotates integrally with the spindle 18. The anvil 8 is provided at a forward position where the front surface of the arms 76, 76 comes into contact with the nylon washer 105 which is externally mounted on the anvil 8 and held by the small cylinder portion 12 a of the gear case 12, and at the step of the front end of the spindle 18 The first cam 87 that rotates together with the anvil 8 is restricted by the vibration switching lever 93 at the retracted position of the anvil 8 because it is housed so as to be movable in the front-rear direction with respect to the retracted position where the rear surface abuts. The vibration drill mode in contact with the second cam 90 is set.

As shown in FIG. 10, in the fourth rotation position of the switching case 64 in which the switching button 30 is positioned at the right end of the window 32, the coupling protrusion 62 is guided by the inclined groove 68 in the clutch switching groove 65. The clutch switching lever 57 is moved backward. Further, in the impact switching groove 84, the stepped pin 83 is at the right end of the first groove 85, and therefore the advance position of the auxiliary ring 78 does not change. However, in the vibration switching groove 101, the connecting protrusion 98 moves backward from the second groove 103 and moves to the left end of the first groove 102. Thus, the vibration switching lever 93 moves backward from the second cam 90.
Therefore, in the fourth position of the switching button 30, the anvil 8 rotates integrally with the spindle 18 and no impact is generated, and the second cam 90 is also in a rotation free state and no vibration is generated. However, the clutch switching lever 57 is retracted. The second internal gear 16 is in a clutch mode that is fixed only by the urging force of the coil spring 50.

  3 and 6A, the steel ball 106 is accommodated together with the coil spring 107, and the steel ball 106 is projected and biased toward the back surface of the switching plate 31. ing. Since the recesses 108, 108,... Corresponding to the four positions of the switching button 30 are provided in the front and rear in the outer circumferential surface of the gear case 12, each operation mode position is set when the switching button 30 is slid. A click action corresponding to the speed switching position is obtained.

On the other hand, a chuck sleeve 109 is externally mounted on the outer periphery of the tip of the anvil 8 so as to be movable back and forth in the axial direction. It is energized. At this retracted position, the ridge 111 protruding from the inner periphery of the chuck sleeve 109 presses the balls 112 and 112 inserted in the anvil 8 so as to be movable back and forth in the radial direction toward the axial center. A bit (not shown) inserted into the insertion hole 113 is prevented from coming off by being protruded into the insertion hole 113 having a hexagonal cross section provided at the shaft center. When the chuck sleeve 109 is slid forward against the bias of the coil spring 110, the pressing of the ball 112 by the protrusion 111 is released, so that the bit can be inserted into and removed from the insertion hole 113.
In particular, here, the chuck sleeve 109 urged backward is brought into contact with the ball bearing 69, so that the anvil 8 is normally in the advanced position by the urge of the coil spring 110, and the first cam 87, the second cam 90, Is maintained in a non-contact state. When the bit mounted on the anvil 8 is pressed against a screw head or the like and the anvil 8 is moved backward, the cam teeth 94 and 95 of the first cam 87 and the second cam 90 come into contact with each other.

  In the impact driver 1 configured as described above, first, when the switch button 30 is operated to the first position to select the drill mode of FIG. 7 and the trigger 10 is pushed in this state and the switch 9 is turned on. The motor 3 is driven and the motor shaft 4 is rotated. Then, the rotation of the motor shaft 4 is decelerated by the planetary gear reduction mechanism 5 and transmitted to the spindle 18. Since the spindle 18 is connected to the anvil 8 not only by the hammer 70 but also by the auxiliary ring 78 in the forward position, the anvil 8 always rotates integrally with the spindle 18 and no impact is generated in the striking mechanism 6. Also in the vibration mechanism 7, since the vibration switching lever 93 is free, no vibration is generated even if the anvil 8 moves backward. Therefore, a drilling operation using a drill bit or the like attached to the anvil 8 is possible. At this time, as described above, since the rotation of the second internal gear 16 is restricted by the clutch switching lever 57, the clutch mechanism does not work, and the rotation of the anvil 8 continues regardless of the load on the anvil 8.

  Next, when the switch button 30 is operated to the second position to select the impact mode of FIG. 8 and the switch 9 is turned on, the rotation of the spindle 18 is transmitted to the anvil 8 via the hammer 70. Therefore, when screwing with a driver bit inserted into the anvil 8, when the load on the anvil 8 is increased, the steel balls 75, 75 are rolled backward along the cam grooves 73, 73 of the spindle 18, The hammer 70 moves backward against the bias of the coil spring 72 and moves away from the arms 76, 76 of the anvil 8. However, at the moment when the engaging claws 77 and 77 are separated from the arms 76 and 76, the coil claws 72 move forward together with the spindle 18 by the bias of the coil spring 72, and the engaging claws 77 and 77 are reengaged with the arms 76 and 76. . By repeating the separation and engagement of the hammer 70 with respect to the anvil 8, the anvil 8 is intermittently hit (impact) in the rotational direction, and tightening is performed. At this time, no vibration is generated in the vibration mechanism 7, and the clutch mechanism does not work by fixing the second internal gear 16.

  Next, when the switching button 30 is operated to the third position to select the vibration drill mode of FIG. 9 and the switch 9 is turned on, the hammer 70 and the anvil 8 are connected by the auxiliary ring 78, so that the striking mechanism 6 No impact occurs and the clutch mechanism does not work by fixing the second internal gear 16. However, in the vibration mechanism 7, the rotation of the second cam 90 is restricted by the vibration switching lever 93. Therefore, when the anvil 8 is moved backward by pressing a drill bit or the like, the first cam 87 that rotates integrally with the anvil 8 is the first cam 87. The anvil 8 is vibrated in the axial direction by contact with the two cams 90 and the cam teeth 94 and 95 interfering with each other.

  When the switch button 30 is operated to the fourth position to select the clutch mode and the switch 9 is turned on, the connection state of the hammer 70 and the anvil 8 by the auxiliary ring 78 does not change, and an impact occurs in the striking mechanism 6. do not do. In addition, since the second cam 90 is also free, no vibration is generated in the vibration mechanism 7 even if the anvil 8 moves backward. However, in the planetary gear speed reduction mechanism 5, since the rotation restriction of the second internal gear 16 by the clutch switching lever 57 is released, the screw tightening proceeds and the load on the anvil 8 and the spindle 18 is pressed by the coil spring 50. Is exceeded, the engagement protrusion 43 of the second internal gear 16 pushes the pressing ring 44 forward to get over the engagement protrusion 46, so that the second internal gear 16 idles and the screw tightening is finished. This clutch operating torque can be adjusted by changing the compression amount of the coil spring 50 by rotating the change ring 53.

In each of the above operation modes, as described above, the switching plate 31 slides to the left and right at the front position by the guidance of the switching button 30 by the window 32, so that the first internal gear 13 together with the speed switching ring 21 is The anvil 8 rotates in a high speed mode in which the planetary gear 14 and the carrier 15 are coupled to each other at the forward movement position in the rotation free state.
On the other hand, if the switching button 30 is retracted only at the first position in the drill mode, the first internal gear 13 is retracted together with the speed switching ring 21 and the rotation is restricted, and meshes only with the planetary gear 14. Therefore, the anvil 8 rotates in the low speed mode. That is, the anvil 8 can be switched between high speed and low speed only in the drill mode.

Thus, according to the impact driver 1 of the said form, it engages simultaneously with the clutch switching lever 57 and the guide body 82 in a housing, and moves the clutch switching lever 57 and the guide body 82 by the movement to a predetermined rotation position. The switching plate 31 and the switching case 64 that can change the combination of the slide positions are provided, and the switching plate 31 and the switching case 64 are rotated by the switching button 30 from the outside of the housing. Since each of the drill modes can be selected, all operation modes can be selected only by operating one switching button 30. Therefore, there is no fear of erroneous operation, and operability and reliability are excellent.
Further, here, a vibration switching lever 93 that switches between applying and releasing the vibration by the vibration mechanism 7 is provided, and this is engaged with the switching case 64, and the sliding position of the vibration switching lever 93 is changed by rotating the switching case 64. By combining them, the seismic drill mode can be further selected. Therefore, even if the seismic drill mode is increased, the operability does not change and good usability can be maintained.

Further, the speed switching ring 21 is indirectly engaged with the switching plate 31 via the speed switching lever 27, and the slide position of the speed switching ring 21 is combined by the forward / backward movement operation of the switching plate 31, so that the drill mode can be used. Since the speed can be switched, the speed can be switched at the same time by the switch button 30, and further improvement in usability can be expected.
Then, the common switching member is formed by the switching case 64, and the movement of each switching member by the switching case 64 is caused by the one-way slits 63, 81, 99 provided in either the gear case 12 or the switching case 64, and the other Switching grooves 65, 84, 101 provided on the connection case, and connection protrusions 62, 98, which are provided in either the switching case 64 or the switching member, and slide the switching member by the guide of the switching groove accompanying the rotation of the switching case 64, and Since each step is performed by the stepped pin 83, each switching member can be reliably guided to the slide position without difficulty.

In addition, the shape of the switching member, the common switching member, the regulation groove, the switching groove, the coupling body, and the like is not limited to the above form, and can be changed as appropriate, for example, the regulation groove provided in the gear case and the switching groove provided in the switching case are in the above form. The design can be changed in various ways, such as changing the sliding direction of the switching member by inverting the V-shaped or trapezoidal protruding side of the switching groove. In particular, the switching member and the common switching member may not be directly engaged but may be indirectly engaged via another member, and the switching member may be formed of a plurality of members.
Further, the striking mechanism is not limited to the structure in which the hammer and the anvil are engaged and disengaged as in the above-described form, but the oil chamber formed in the case due to the speed difference between the input side case and the output side spindle. Even a striking mechanism using a well-known oil unit that intermittently strikes the spindle in the rotational direction by pressure, has a striking release release means that switches between the case and the output shaft being integrated or separated. If so, the switching member can be similarly slid by the common switching member of the present invention.

  Further, in the above embodiment, the impact driver that can select four operation modes of the drill mode, the impact mode, the vibration drill mode, and the clutch mode has been described, but these four operation modes are not essential, and at least the impact mode and The impact tool that can select the clutch mode and the drill mode (corresponding to claim 1), or the impact tool that can select at least the impact mode, the drill mode and the vibration drill mode (corresponding to claim 3) If so, other power tools can be employed. Therefore, the vibration drill mode is not essential for the former impact tool, and the clutch mode is not essential for the latter impact tool.

On the other hand, in the above mode, the switching button is retracted only in the drill mode so as to obtain the low speed mode. However, the switching button can be retracted in some or all of the other operation modes so that the low speed and the high speed can be achieved. Switching may be possible. In addition, the speed switching is obtained at the front and rear positions of the speed switching member by the front and rear operation of the switching plate, but if the speed switching is performed only in some operation modes, it is the same as in other operation modes. The speed switching member can be slid by the restriction groove provided in either the gear case or the switching case, the switching groove provided in the other, and the connecting body provided in either the switching case or the switching member. You can also.
Of course, the present invention can be applied even to an impact tool without such a speed switching mechanism, but in this case, it is necessary to form a common switching member with a switching plate that can move back and forth and a switching case that only rotates. However, a single member in which the switching plate is integrated with the switching case is sufficient.

It is a longitudinal cross-sectional view of an impact driver. It is a disassembled perspective view of an internal mechanism. It is a disassembled perspective view of an internal mechanism. It is a top view of an impact driver. (A) is a side view of a gear case part, (B) is an AA sectional view. (A) is a BB line sectional view, (B) is a CC line sectional view, and (C) is a DD line sectional view. The top is a side view of the gear case portion in the drill mode, and the bottom is a longitudinal sectional view (however, the change ring and the hammer case are shown). The top is a side view of the gear case portion in the impact mode, and the bottom is a longitudinal sectional view (however, the change ring and the hammer case are shown). The top is a side view of the gear case portion in the vibration drill mode, and the bottom is a longitudinal sectional view (however, the change ring and the hammer case are shown). The top is a side view of the gear case portion in the clutch mode, and the bottom is a longitudinal sectional view (however, a change ring and a hammer case are shown).

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Impact driver, 2 ... Body housing, 3 ... Motor, 4 Motor shaft, 5 ... Planetary gear reduction mechanism, 6 ... Stroke mechanism, 7 ... Vibration mechanism, 8 ... Anvil, 12 ... Gear case, 13 ... First internal Gear, 16 second internal gear, 18 spindle, 21 speed switching ring, 27 speed switching lever, 30 switching button, 31 switching plate, 32 window, 44 pressing ring, 53 change ring, 57 ... Clutch switching lever, 62, 98 Connection protrusion, 64 ... Switching case, 65 ... Clutch switching groove, 70 ... Hammer, 78 ... Auxiliary ring, 83 ... Stepped pin, 84 ... Impact switching groove, 87 ... First cam , 90, second cam, 93, vibration switching lever, 101, vibration switching groove.

Claims (5)

  1. A motor and a planetary gear speed reduction mechanism are provided in the housing, and the output of the motor can be transmitted to the output shaft protruding forward of the housing via the planetary gear speed reduction mechanism. While one internal gear of the gear reduction mechanism is rotatably provided and provided with pressing means for pressing and fixing the internal gear,
    In the housing, a striking mechanism capable of intermittently striking the output shaft in the rotation direction, and a release means capable of arbitrarily releasing striking to the output shaft by the striking mechanism are provided internally,
    A clutch switching member that is slidable between a first slide position that engages with the internal gear and restricts rotation thereof, and a second slide position that releases the rotation restriction away from the internal gear; Slide between a first slide position where the release means is operated to release the impact applied by the impact mechanism and a second slide position where the impact is applied by the impact mechanism without operating the release means It is an impact tool with each possible impact switching member,
    In the housing, a common switching member that engages with the clutch switching member and the impact switching member at the same time, moves the both switching members by moving to a predetermined position, and can change the combination of the slide positions, By operating the common switching member to move from the outside of the housing, an impact mode in which the impact is imparted by the impact mechanism and the rotation of the internal gear are simultaneously controlled, the impact impartment by the impact mechanism is released, and the internal gear is operated. An impact tool characterized by being able to select a clutch mode for simultaneously releasing the rotation restriction and a drill mode for simultaneously releasing the impact imparted by the striking mechanism and restricting the rotation of the internal gear.
  2.   In the housing, there is a vibration mechanism capable of applying a vibration in the axial direction to the output shaft, and a second release means capable of arbitrarily releasing the vibration applied to the output shaft by the vibration mechanism. The first slide position for releasing the vibration imparted by the vibration mechanism by operating the second release means, and the second slide for applying the vibration by the vibration mechanism without operating the second release means By providing a vibration switching member that is slidable between positions, engaging it with the common switching member, and combining the sliding position of the vibration switching member by the movement operation of the common switching member, it is possible to give a hit by the striking mechanism 2. The impact tool according to claim 1, wherein a seismic drill mode that simultaneously cancels the rotation and restricts rotation of the internal gear and imparts vibration by the vibration mechanism can be further selected.
  3. A motor and a planetary gear reduction mechanism are installed in the housing, and the output of the motor can be transmitted to an output shaft protruding forward of the housing via the planetary gear reduction mechanism, and the output A striking mechanism capable of intermittently striking the shaft in the rotational direction, a releasing means capable of arbitrarily releasing the striking of the output shaft by the striking mechanism, and a vibration in the axial direction can be imparted to the output shaft And a second release means capable of arbitrarily releasing the vibration imparted to the output shaft by the vibration mechanism,
    Slide between a first slide position where the release means is operated to release the impact applied by the impact mechanism and a second slide position where the impact is applied by the impact mechanism without operating the release means A possible impact switching member, a first slide position that releases the vibration imparted by the vibration mechanism by operating the second release means, and a vibration imparted by the vibration mechanism without operating the second release means Each of the impact tools provided with a vibration switching member that can slide between the second slide position and
    In the housing, a common switching member that engages with the impact switching member and the vibration switching member at the same time, moves the both switching members by moving to a predetermined position, and can change the combination of the slide positions, By operating the common switching member to move from the outside of the housing, an impact mode for simultaneously applying the impact by the impact mechanism and releasing the motion by the vibration mechanism, and releasing the impact by the impact mechanism and the vibration mechanism An impact tool characterized by enabling selection of a drill mode for simultaneously releasing the vibration imparting by the shock and a vibration drill mode for simultaneously releasing the shock imparted by the striking mechanism and the vibration imparting by the vibration mechanism.
  4.   The planetary gear speed reduction mechanism can be slid between a coupling position where the other internal gear is coupled to one of the front and rear carriers and a coupling release position where the coupling between the internal gear and the carrier is released. In the case where the speed switching member is provided, the speed switching member is engaged with the common switching member, and the sliding position of the speed switching member is combined by a movement operation of the common switching member. The impact tool according to any one of claims 1 to 3, wherein the speed can be switched.
  5.   The common switching member is formed by a switching case that is provided on the outer periphery of the gear case that accommodates the planetary gear speed reduction mechanism and the striking mechanism and moves by operating a switching button that is exposed to the outside of the housing, and each switching member is moved by the switching case. A one-way restricting groove provided in one of the gear case and the switching case, a switching groove provided in the other and having a direction different from that of the restricting groove, and passing through the restricting groove and the switching groove. Or a connecting member that is provided on any one of the switching members and that slides the switching member along the restriction groove by a guide of the switching groove accompanying the movement of the switching case. 4. The impact tool according to any one of 4.
JP2004314598A 2004-10-28 2004-10-28 Impact tools Active JP4468786B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2004314598A JP4468786B2 (en) 2004-10-28 2004-10-28 Impact tools

Applications Claiming Priority (10)

Application Number Priority Date Filing Date Title
JP2004314598A JP4468786B2 (en) 2004-10-28 2004-10-28 Impact tools
US11/251,987 US7308948B2 (en) 2004-10-28 2005-10-18 Electric power tool
EP06016661A EP1716978B1 (en) 2004-10-28 2005-10-19 Electric power tool
EP09008269A EP2103390B1 (en) 2004-10-28 2005-10-19 Impact wrench with switching member for selecting a drill mode or an impact mode
EP20050022802 EP1652630B1 (en) 2004-10-28 2005-10-19 Electric power tool with switching member for selecting one operation mode among various operation modes
DE200560004980 DE602005004980T2 (en) 2004-10-28 2005-10-19 Power tool with operating mode selector switch for selecting one of several operating modes
DE200560018170 DE602005018170D1 (en) 2004-10-28 2005-10-19 power tool
CN 200510114289 CN100354074C (en) 2004-10-28 2005-10-21 Electric power tool
US11/905,928 US7380613B2 (en) 2004-10-28 2007-10-05 Electric power tool
US11/905,935 US7380612B2 (en) 2004-10-28 2007-10-05 Electric power tool

Publications (2)

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JP2006123080A true JP2006123080A (en) 2006-05-18
JP4468786B2 JP4468786B2 (en) 2010-05-26

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CN1765590A (en) 2006-05-03
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