JP2010052101A - Rotary impact tool - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rotary impact tool which attains cost reduction by reducing the number of components and is usable as a driver drill. <P>SOLUTION: The rotary impact tool includes a spindle 3, a hammer 5, an anvil 7 receiving a rotative force and striking power from the hammer 5, a hammer biasing spring for biasing the hammer 5 toward the anvil 7, a clutch 12 for disabling torque transmission to the spindle 3 from a motor 1 when load torque exceeding a predefined value is activated between the motor 1 and the spindle 3, and a torque adjustment spring for adjusting the torque at an actuation start of the clutch 12. In the rotary impact tool, the hammer biasing spring and the torque adjustment spring are integrated into one common spring 4. The hammer 5 is disposed in front of the spring 4 and the clutch 12 is disposed at the rear of the spring. The torque of the spindle 3 necessary for the hammer 5 to initiate striking by a cam mechanism is set larger than the torque of the spindle 3 to operate the clutch 12. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a rotary impact tool, and more particularly to a rotary impact tool having an improved clutch mechanism.

  An electric tool that can also be used as a driver drill is known, for example, in Patent Document 1. In patent document 1, in order to use an electric tool as a driver drill, the clutch using the planetary gear mechanism is provided. On the other hand, products with a clutch mechanism added to rotary impact tools such as impact drivers are on the market. In the rotary impact tool having the clutch function, it is important that the impact mechanism is not activated when the clutch is activated. The configuration of such a conventional example will be described with reference to FIGS.

  FIG. 5 is a cross-sectional view showing the main part of a rotary impact tool that can also be used as a conventional driver drill. Here, the vertical direction and the front-rear direction will be described as indicating the directions shown in the drawing. The rotational force of the motor 101 is transmitted to the spindle 103 via the planetary gear mechanism 102. The spindle 103 and the hammer 105 are connected by a cam mechanism constituted by a cam ball 106 and a V-shaped cam groove, and the hammer 105 is always urged forward by a hammer urging spring 104. The anvil 107 and the hammer 105 mesh with each other in the rotation direction between the hammer convex portion 105a and the anvil convex portion 107a. An elastic stopper 108 is installed between the spindle 103 and the hammer 105. The ring 109 that restricts the retraction of the hammer 105 includes an inner ring 109 a and an outer ring 109 b, which are held by the switching knob 110, and are movable in the axial direction together with the switching knob 110. A ball 111 is disposed between the inner ring 109 a and the outer ring 109 b, and the inner ring 109 a can rotate in the circumferential direction together with the hammer 105.

  The clutch 112 includes a ring gear 113, a flange 114, a torque adjustment spring 115, and a nut 116. The rear end of the flange 114 is in contact with the ring gear 113, and the ring gear 113 and the flange 114 are each formed with a trapezoidal convex portion. The flange 114 is urged rearward (motor 1 side) in the rotational axis direction by a torque adjustment spring 115 via a washer 123. The torque adjustment spring 115 is held by a nut 116. A threaded portion is formed on the inner peripheral side of the nut 116 and is screwed with a threaded portion formed on the outer peripheral side of the case 118. The nut 116 contacts the axially extending rib formed on the inner peripheral side of the dial 117 at four locations on the circumferential side of the nut 116, and the nut 116 moves forward or backward in the axial direction when the operator rotates the dial 117. Then, the compression height of the torque adjustment spring 115 is adjusted.

  The operation of the rotation hitting with the above configuration will be described. When the spindle 103 and the hammer 105 are relatively twisted by the reaction force received through the screw from the member to be tightened, the hammer 105 is energized by a cam mechanism, that is, a V-shaped cam groove cut into a V shape. Retraction starts while the spring 104 is contracted. When the hammer 105 starts retreating and climbs over the height of the anvil projection 107 a, the engagement with the anvil 107 is released, and the hammer 105 rotates and advances while being accelerated by the hammer urging spring 104. Further, the hammer 105 and the anvil 107 respectively have hammer convex portions 105a and anvil convex portions 107a that are symmetrically disposed at two positions on the rotation plane, and the hammer convex portion 105a and the anvil convex portion 107a are engaged with each other in the rotation direction. It is in. The rotational striking force is transmitted by the engagement between the convex portions. With the above configuration, the rotary hitting operation proceeds as follows. The rotational force of the spindle 103 is transmitted to the hammer 105 through the cam mechanism and starts to rotate together. The protrusions of the hammer 105 and the anvil 107 engage with each other before the half rotation. When the reaction force received from the end tool side is weak, the rotation is performed as it is. However, when the reaction force is increased, the spindle 103 and the hammer 105 are twisted relatively, and the hammer 105 retracts while the hammer biasing spring 104 is contracted. Begin. Eventually, the height of the convex part can be overcome and the meshing can be solved. The hammer 105 is accelerated in the rotational direction by the elastic energy stored in the hammer biasing spring 104 in addition to the rotational force of the spindle 103 and starts to advance. While the hammer 105 is accelerated, the convex portions are fitted again. At this time, a strong rotational striking force is applied to the anvil 107 and transmitted to the tightened member. And again, the hammer 105 starts to retreat. The stopper 108 is made of an elastic material so that the hammer 105 does not directly contact the spindle 103 and break.

  By moving the switching knob 110 forward (anvil 107 side), the ring 109 moves to the hammer 105 side as shown in FIG. FIG. 6 shows a state in which the operation of the hammer 105 is limited and used as a drill. When a strong reaction force is received from the tip tool side, the hammer 105 tries to move to the motor 101 side by the cam mechanism, but since the movement is restricted by the ring 109, the hammer 105 is not hit. The ring gear 113 is regulated in the rotational direction by the convex portion of the flange 114. However, when the transmission torque of the motor 101 and the spindle 103 exceeds a certain level, the torque adjusting spring 115 biases the flange 114 toward the ring gear 113 side. Since the force of the convex part of the flange 114 overcoming the convex part of the ring gear 113 exceeds, the flange 114 moves to the torque adjustment spring 115 side, the convex part is disengaged, and the ring gear 113 rotates. As a result, the motor 101 and the spindle 103 are in a state where torque transmission is impossible, that is, a state where the clutch is operated.

  Since the height of the torque adjustment spring 115 changes by turning the dial 117 at this time, the transmission torque of the clutch 112 can be adjusted. Further, as shown in FIG. 6, the dial 117 is further turned to tighten the nut 116 until it contacts the washer 123, thereby restricting the axial movement of the flange 114 and making the ring gear 113 completely non-rotatable. It can be disabled and a rotary impact tool can be used as a drill.

  Further, as shown in FIG. 7, the switching knob 110 is rotated and moved rearward (motor 1 side), the hammer 105 is released from the striking stop state, and at the same time, the dial 117 is rotated to restrict the axial movement of the flange 114 and the clutch. By stopping the operation of 112, the hammer 105 can be struck and the machine can be used as a rotary impact tool.

Japanese Patent Laying-Open No. 2005-205569

  Since the conventional rotary impact tool described with reference to FIGS. 5 to 7 can be used as a driver drill with a clutch in addition to the impact tool with a single tool, a user-friendly tool can be realized. However, since a total of two springs are required for hammer energization and clutch torque adjustment, the number of parts increases, the manufacturing cost increases, and the tool body increases. Moreover, since two dials are required, the number of parts increases. Therefore, it was a manufacturer's request that the main body should be made smaller and realized at a lower cost.

  The present invention has been made in view of the above background, and an object thereof is to achieve a reduction in the size of a rotary impact tool that can be used as a driver drill.

  Another object of the present invention is to provide a rotary impact tool that can be used as a driver drill and has a reduced cost by reducing the number of parts.

  Still another object of the present invention is to provide a rotary impact tool that is easy to use by switching between a mode in which hammering is stopped and a mode in which the operation of a clutch is stopped with a single operating means.

  Of the inventions disclosed in the present application, typical features will be described as follows.

 According to one aspect of the present invention, a motor, a spindle rotated by the motor, a hammer that moves in the axial direction of the spindle while rotating by the action of a cam mechanism provided on the spindle, and rotational force and impact by the hammer. An anvil to which force is applied, a hammer biasing spring that biases the hammer toward the anvil, a clutch that disables torque transmission from the motor to the spindle when a load torque of a predetermined level or more is actuated between the motor and the spindle, In the rotary impact tool having a torque adjusting spring for adjusting the operation starting torque of the clutch, the hammer biasing spring and the torque adjusting spring are realized by one common spring. A hammer is positioned in front of the common spring and a clutch is positioned in the rear. The spindle torque necessary for the hammer to start hitting with the cam mechanism is set to be larger than the torque of the spindle on which the clutch operates.

  According to another aspect of the present invention, the clutch includes a planetary gear mechanism having a ring gear, a convex portion formed on the ring gear, a ball and a needle that are engaged with the convex portion and are urged toward the motor by a common spring. A clutch stopping means configured to stop the operation of the clutch is provided. Further, the hammer stopping means for stopping the operation of the hammer is provided, and the ON / OFF control of the operation of the clutch stopping means and the hammer stopping means is realized by a common operation means. The common operating means can be realized by, for example, a dial-type operating means that rotates coaxially with the rotating shaft, and it is preferable to adjust the hammering torque amount by the hammer and the clutch operating torque amount by this operating means. .

  According to still another aspect of the present invention, the clutch stopping means includes a recess formed in the ring gear and a pin that can be inserted into the recess and movable in the axial direction, and the clutch is configured by limiting the rotation of the ring gear by the pin. It was comprised so that the operation | movement of could be stopped. The pins are provided at a plurality of positions in the axial direction of the ring gear, and are urged by a spring in a direction of being detached from the recess of the ring gear. The striking stop means is formed on the anvil and is formed separately from the output shaft portion that holds the tip tool, and the wing portion that can move in the axial direction while rotating synchronously with the output shaft portion, and the hammer is moved to move the hammer And a flange for retreating.

  According to the first aspect of the present invention, the spring normally used as a hammer biasing spring is configured to serve as a torque adjustment spring, so that not only the number of parts can be reduced but also the main body can be miniaturized.

  According to the second aspect of the present invention, the hammer is located in front of the common spring and the clutch is located in the rear, so that the common spring serves as a hammer biasing spring and a torque adjustment spring. realizable.

  According to the third aspect of the present invention, since the torque of the spindle necessary for the hammer to start striking with the cam mechanism is set to be larger than the torque of the spindle on which the clutch operates, the operation of the clutch is stopped. If not, the clutch is operated prior to hammering, so the parts for stopping hammering can be omitted, and the main body can be downsized.

  According to the invention described in claim 4, the clutch includes a planetary gear mechanism having a ring gear, a convex portion formed on the ring gear, a ball and a needle that are engaged with the convex portion and are urged to the motor side by a common spring. Since it is configured, a clutch mechanism can be realized with a simple configuration using a planetary gear mechanism.

  According to the fifth aspect of the present invention, since the clutch stop means for stopping the operation of the clutch is provided, the hammer biased by the common spring can be operated by stopping the operation of the clutch. That is, the clutch stop mechanism can function as a hammer operation switch under the condition that the spindle torque required for the hammer to start striking with the cam mechanism is greater than the torque of the spindle on which the clutch operates.

  According to the sixth aspect of the present invention, since the hammer stop means for stopping the operation of the hammer is provided, it can be used as a normal drill. Further, by stopping the operation of the hammer, the set torque at which the clutch operates can be arbitrarily set within a predetermined range.

  According to the seventh aspect of the present invention, since the common operation means for controlling ON / OFF of the operation of the clutch stop means and the impact stop means is provided, these operations can be operated by one operation means, so that the usability is improved. good.

  According to the invention described in claim 8, since the common operating means also adjusts the hammering torque by the hammer and the operating torque of the clutch, the operating means 1 provided on the outer peripheral side of the anvil of the rotary impact tool. All you need is a compact tool.

  According to the ninth aspect of the present invention, the clutch stopping means includes a recess formed in the ring gear and a pin that can be inserted into the recess and movable in the axial direction, and the rotation of the ring gear is limited by the pin. Since the operation is stopped, the clutch stopping means can be realized only by adding a simple configuration to the planetary gear mechanism, and the rotary impact tool can be made compact because only a small part needs to be added.

  According to the tenth aspect of the present invention, the pins are provided at a plurality of positions in the axial direction of the ring gear, and are urged by the springs in the direction away from the recesses of the ring gear. Since it can be pressed by the means and can be separated from the recess of the ring gear by the spring, the clutch stopping means can be realized with a simple configuration.

  According to the invention of claim 11, the hitting stop means includes a wing portion that is formed separately from the output shaft portion that holds the tip tool and is movable in the axial direction while rotating synchronously with the output shaft portion, and the wing portion. Since it is configured to include a flange that moves and retracts the hammer, it is possible to reliably prevent the hammer from being hit and to realize a highly reliable rotary hitting tool.

  The above and other objects and novel features of the present invention will become apparent from the following description and drawings.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following drawings, parts having the same function are denoted by the same reference numerals, and repeated description is omitted. Further, in the present specification, description will be made assuming that the vertical direction is the direction shown in FIG.

  FIG. 1 is a structural sectional view showing an embodiment of the rotary impact tool of the present invention. The anvil 7 includes a wing portion 7a and an output shaft portion 7b, and the wing portion 7a is connected to the output shaft portion 7b so as to be movable in the axial direction. At the front end of the output shaft portion 7b, a tip tool holding portion 7c having a hexagonal cross section in the axial direction for mounting the tip tool is formed. A screw portion is formed on the outer peripheral side of the case 18, and is screwed with the screw portion formed on the inner peripheral side of the nut 16. The flange 14 is arranged so that the front is supported by the nut 16 and the rear is in contact with the wing 7a. A dial 17 is provided on the outer periphery of the nut 16 and the case 18, and the dial 17 is fixed to the housing 19 so as to be rotatable in the circumferential direction. The nut 16 is fixed in the circumferential direction by a rib 17a formed on the inner peripheral side of the dial 17 so as to extend in the circumferential direction.

  The clutch 12 includes a ring gear 13, an uneven portion 13a formed at four locations in the circumferential direction of the front end surface of the ring gear, a ball 22 that engages with the uneven portion 13a, and an annular needle that is attached to the front end side of the ball 22. 24 and a spring 4 that urges the needle 24 rearward in the axial direction via a washer 23. The spring 4 also functions to urge the hammer 5 forward in the axial direction and functions as a common spring for the clutch and the hammer. In this embodiment, the torque required for the hammer 5 to get over the wing portion 7a of the anvil 7 is greater than the torque required for the ring gear 13 to rotate by disengagement of the concave-convex portion 13a and the ball 22. Is configured.

  Pins 20 provided at two locations on the upper and lower sides of the planetary gear mechanism 2 are installed so as to be movable in the axial direction so that they can be inserted into and removed from the recesses provided in the case of the planetary gear mechanism 2. A flange portion 20a having a large diameter is formed. A small-diameter spring 21 is coaxially disposed behind the flange portion 20 a of the pin 20, and the pin 20 is biased forward by the small-diameter spring 21. There are recesses 13 b at two locations on the outer periphery of the ring gear 13, and the pin 20 can move into a hole formed by the recess provided in the case of the planetary gear mechanism 2 and the recess 13 b of the ring gear 13. On the inner peripheral side of the dial 17, a convex portion 17 b protruding rearward in the axial direction is formed. When the dial 17 is rotated and comes to a position where the convex portion 17 b contacts the pin 20, the pin 20 is pressed backward, The pin 20 moves rearward against the pressing force of the small-diameter spring 21 and engages with the concave portion 13b of the ring gear 13, thereby preventing the ring gear 13 from rotating. The fact that the ring gear 13 does not rotate means that the clutch 12 does not operate, and the pin 20 is a main part of the clutch stopping means.

  On the other hand, by rotating the dial 17, the rib 17 a formed on the inner peripheral side of the dial 17 rotates the nut 16, and the nut 16 moves in the axial direction by the action of the thread formed on the case 18. The flange 14 whose front end is supported by the nut 16 moves in the axial direction together with the nut 16 and moves the wing portion 7a of the anvil 7 in the axial direction. The wing portion 7a moves rearward (motor 1 side) and moves the hammer 5 rearward until it hits a stopper 8 made of an elastic body. In this way, the hammering stop mode can be realized by moving the hammer 5 backward.

  The convex portion 17b of the dial 17 is installed so that the convex portion 17b moves the pin 20 rearward (motor 1 side) at the position where the nut 16 is most advanced and the position where the nut 16 is most retracted. In the present embodiment, the pins 20 are provided at two locations separated by 180 degrees in the circumferential direction. 4 is a perspective view showing the shape of the dial 17, (1) is a rear view of the dial 17 viewed from the vicinity of the AA portion in FIG. 2, and (2) is a B- in FIG. 4 (1). It is sectional drawing of the B section. The dial 17 is formed with a through hole 17c penetrating the case 18 in the center, and ribs 17a extending in the axial direction are formed at four locations spaced 90 degrees in the circumferential direction on the inner peripheral wall which is the outer periphery of the through hole. . On the inner side in the vicinity of the rear end of the dial 17, convex portions 17 b that protrude backward are formed at two locations that are 180 degrees apart rearward in the axial direction. When the convex portion 17b pushes the pin 20 rearward in the axial direction, the pin 20 is inserted into the concave portion 13b of the ring gear 13. A groove portion 17 d for engaging with the housing 19 is formed on the outer peripheral side near the rear end of the dial 17.

  Next, operations of the striking mechanism and the clutch mechanism according to the present embodiment will be described with reference to FIGS. FIG. 1 shows a state where the striking mechanism is operated and the clutch is stopped. As shown in FIG. 1, when the nut 16 is located at the foremost position, the pin 20 is moved rearward, so that the rotation of the ring gear 13 is restricted by the pin 20, and the clutch does not operate. Further, in the state of FIG. 1, the wing portion 7a is located in the front, and the backward movement of the hammer 5 is not limited. Therefore, when the anvil 7 receives a reaction force exceeding a predetermined torque from the tip tool, the spindle 3 and the hammer 5 The hammer 5 starts to move backward while the hammer biasing spring 4 is contracted. After that, the hammer 5 gets over the wing part 7a of the anvil 7, and the meshing between them is released. The hammer 5 is accelerated in the rotational direction by the elastic energy stored in the spring 4 in addition to the rotational force of the spindle 3 and starts moving forward. While the hammer 5 is accelerated, the convex portions are fitted again. At this time, a strong rotational impact force is transmitted to the wing portion 7 a of the anvil 7. Since the wing portion 7a and the output portion 7b are fixed in the rotational direction, the striking force is transmitted to the tip tool.

  FIG. 2 shows a state where the striking mechanism is stopped and the clutch is operated. As shown in FIG. 2, the pin 17 is moved forward by the force of the small diameter spring 21 by rotating the dial 17 and releasing the urging force by the convex portion 17 b. As a result, the fixed state of the ring gear 13 is released and the ring gear 13 can be rotated. In the state shown in FIG. 2, the striking mechanism is operable, but as described above, the torque required for the hammer 5 to get over the wing 7a is because the ring gear 13 rotates with the projection 13a and the ball 22 disengaged. Since the shape of the hammer 5, the configuration and arrangement of the cam mechanism, the shape of the concavo-convex portion 13a of the ring gear 13, the size of the ball 22 and the like are set so as to be larger than the necessary torque, the hammer 5 is started to hit. The clutch 12 operates before the operation. Therefore, the striking mechanism is substantially stopped, and the clutch 12 operates.

  In a state in which the clutch 12 is operated, the spring 17 is compressed by rotating the dial 17 and moving the nut 16 further rearward, so that the operation starting torque of the clutch 12 can be increased. By this adjustment, it is possible to adjust the tightening torque by the tip tool. Since the spring 4 is shared with the urging spring of the hammer 5, the compression torque of the spring 4 increases the operating torque of the clutch 12 and the torque for the hammer 5 to get over the wing 7 a at the same rate. The clutch 12 always operates without starting hitting with the hammer 5. Thereby, the rotary impact tool can be used as a driver.

  FIG. 3 shows a state in which both the striking mechanism and the clutch are stopped. The dial 17 is further rotated from the state of FIG. 2, and the hammer 5 is brought into contact with the stopper 8 as shown in FIG. In this state, the hammer 5 tries to get over the wing 7a. However, since the rearward movement is restricted by the stopper 8, the fitting between the hammer 5 and the wing 7a is not released. 7a rotates together. Thereby, the rotational force from the spindle 3 is directly transmitted to the output unit 7b. Further, since the convex portion 17b of the dial 17 moves the pin 20 to the motor 1 side, the rotation of the ring gear 13 is restricted, and the clutch 12 also does not operate. As a result, the rotary impact tool is not hit, the clutch is not actuated, and can be used as a drill.

  As is clear from the above description, according to the present invention, the hammer biasing spring and the torque adjustment spring can be realized by one common spring, so that it is possible to reduce the size of the rotary impact tool that can be used as a driver drill, Cost reduction was realized by reducing the number of parts.

  In addition, since the hammer stopping means for stopping hammering and the clutch stopping means for stopping the operation of the clutch are realized by one operation dial, a user-friendly rotary hitting tool can be realized.

  As mentioned above, although demonstrated based on embodiment which shows this invention, this invention is not limited to the above-mentioned form, A various change is possible within the range which does not deviate from the meaning. For example, in this embodiment, a rotary impact tool using an electric motor has been described. However, the present invention can also be applied to a rotary impact tool using an air motor. Further, in order to limit the operation of the clutch 12, the pin 20 that moves in the axial direction is used. However, the pin 20 is not limited to the pin 20, and the rotation of the ring gear 13 can be limited or released by any member. good.

It is a fragmentary sectional view showing the rotary impact tool concerning the embodiment of the present invention, and shows the state where the impact mechanism is operated and the clutch is stopped. It is a fragmentary sectional view which shows the rotary impact tool which concerns on embodiment of this invention, and shows the state in the case of stopping an impact mechanism and operating a clutch. It is a fragmentary sectional view which shows the rotary impact tool which concerns on embodiment of this invention, and shows the state in the case of stopping both an impact mechanism and a clutch. It is a perspective view which shows the single-piece | unit shape of the dial 17 of FIG. 1, (1) is a rear view seen from the AA part vicinity of FIG. 2, (2) is BB part of FIG. 4 (1). It is sectional drawing. It is a fragmentary sectional view which shows the rotary impact tool of a prior art example, and shows the state at the time of using a rotary impact tool as a driver. It is a fragmentary sectional view which shows the rotary impact tool of a prior art example, and shows the state at the time of using a rotary impact tool as a drill. It is a fragmentary sectional view which shows the rotary impact tool of a prior art example, and shows the state at the time of using as a rotary impact tool.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Motor 2 Planetary gear mechanism 3 Spindle 4 Spring 5 Hammer 5a Hammer convex part 6 Cam ball 7 Anvil 7a (Anvil) feather | wing part 7b (Anvil) output part 7a (Anvil) tip tool holding part 8 Stopper 12 Clutch 13 Ring gear 13a Concave and convex portions (ring gear) 14 Flange 16 Nut 17 Dial 17a (Dial) rib 17b (Dial) convex portion 17c (Dial) through hole 17c
17d (dial) groove portion 18 case 19 housing 20 pin 20a (pin) flange portion 21 small diameter spring 22 ball 23 washer 101 motor 102 planetary gear mechanism 103 spindle 104 hammer biasing spring 105 hammer 105a hammer convex portion 106 cam ball 107 anvil 107a Anvil convex part 108 Stopper 109 Ring 110 Switching knob 111 Ball 12 Clutch 113 Ring gear 114 Flange 115 Torque adjustment spring 116 Nut 117 Dial 118 Case

Claims (11)

A motor, a spindle rotated by the motor, a hammer that moves in the axial direction of the spindle while rotating by the action of a cam mechanism provided on the spindle, and an anvil to which a rotational force and a striking force are given by the hammer A hammer biasing spring that biases the hammer toward the anvil, and a clutch that disables torque transmission from the motor to the spindle when a load torque of a predetermined level or more is activated between the motor and the spindle; In the rotary impact tool having a torque adjustment spring for adjusting the operation starting torque of the clutch,
The rotary impact tool characterized in that the hammer biasing spring and the torque adjusting spring are realized by one common spring.   2. The rotary impact tool according to claim 1, wherein the hammer is positioned in front of the common spring and the clutch is positioned in the rear.   The rotary hammer according to claim 1 or 2, wherein a spindle torque required for the hammer to start hitting by the cam mechanism is set to be larger than a spindle torque for operating the clutch. tool.   The clutch includes a planetary gear mechanism having a ring gear, a convex portion formed on the ring gear, and a ball and a needle that are engaged with the convex portion and are urged toward the motor by the common spring. The rotary impact tool according to claim 3.   The rotary impact tool according to claim 4, further comprising clutch stop means for stopping the operation of the clutch.   6. The rotary impact tool according to claim 5, further comprising impact stop means for stopping the operation of the hammer.   The rotary impact tool according to claim 6, further comprising a common operation means for controlling ON / OFF of operations of the clutch stop means and the impact stop means.   The rotary hitting tool according to claim 7, wherein the common operating means further adjusts the hitting torque by the hammer and the operating torque of the clutch.   The clutch stop means includes a recess formed in the ring gear and a pin that can be inserted into the recess and movable in the axial direction, and the rotation of the ring gear is limited by the pin to stop the operation of the clutch. The rotary impact tool according to claim 5.   The rotary impact tool according to claim 9, wherein the pin is provided at a plurality of locations in the axial direction of the ring gear, and is urged by a spring in a direction away from the recess of the ring gear.   The striking stop means is formed separately from an output shaft portion that holds a tip tool, and a wing portion that is movable in the axial direction while rotating synchronously with the output shaft portion, and the hammer is moved backward by moving the wing portion. The rotary impact tool according to claim 6, comprising a flange to be moved.

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