JP5283231B2 - Rotating tool - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To surely prevent falling of a carrier of an input side shift part, and to achieve further compactification of an axial direction dimension of the whole of a speed reduction mechanism. <P>SOLUTION: A rotating tool incorporates the input side shift part and an output side shift part constituted of planetary speed reduction mechanisms by connecting the shift parts in series in the axial direction. The input side shift part includes a carrier restraining member for restraining an axial direction position of the carrier, and a ring gear slidably provided in the axial direction to switch a speed reduction state and a non-speed reduction state. The output side shift part includes a sun gear and a moving member connected to the sun gear to be slidable in the axial direction to switch the speed reduction state and a non-speed reduction state. The carrier of the input side shift part and the moving member are connected to be slidable in the axial direction. The carrier restraining member is arranged in a portion except a region held in the axial direction by mutual abutting surfaces of the carrier of the input side shift part and the moving member. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

  The present invention relates to a rotary tool incorporating a multi-stage planetary reduction mechanism.

  In a rotary tool incorporating a plurality of stages of planetary speed reduction mechanisms, it is common that the speed reduction ratio can be changed by sliding components provided in the planetary speed reduction mechanism in the axial direction.

  For example, in the rotary tool described in Patent Document 1, the sun gear of the second stage planetary reduction mechanism is slid together with the drive carrier to switch between the deceleration state and the non-deceleration state of the second stage planetary reduction mechanism; It has become.

  Further, in the rotary tool described in Patent Document 2, the ring gear included in the first stage planetary reduction mechanism is slid in the axial direction to switch between the deceleration state and the non-deceleration state of the first stage planetary reduction mechanism; (Refer to Form 2 described in FIG. 5 and the like).

  By the way, the present inventors have invented a rotary tool as shown in FIG. The speed reduction mechanism built in the rotary tool is one in which an input side transmission unit 3 and an output side transmission unit 5 each including a planetary reduction mechanism are connected in series in the axial direction. Note that a more detailed structure of the speed reduction mechanism shown in FIG. 10 will be described in [Mode for Carrying Out the Invention] of the present invention to be described later, so only a brief description will be given here.

  The input side transmission unit 3 of the speed reduction mechanism is configured to switch between a deceleration state and a non-deceleration state of the input side transmission unit 3 by providing a ring gear 33 slidably in the axial direction. In the output side transmission unit 5 of the speed reduction mechanism, the sun gear 51 and the moving member 40 (transmission carrier 42, etc.) connected thereto are provided so as to be slidable in the axial direction. It is structured to switch between the deceleration state and the non-deceleration state. And the carrier 35 of the input side transmission part 3 and the said moving member 40 are connected via the torque transmission member 41 so that sliding is possible in an axial direction.

  In the rotary tool incorporating the deceleration mechanism as shown in FIG. 10, the deceleration state and non-deceleration state of the input side transmission unit 3 and the deceleration state and non-deceleration state of the output side transmission unit 5 are appropriately combined. Thus, it is possible to switch to various reduction ratios. In addition, since the drill driver mode and the impact driver mode are further switched in conjunction with the slide of the moving member 40, the mode can be switched simultaneously with the reduction ratio switching operation, and the overall mechanism can be enlarged. There is an advantage that it is suppressed.

  By the way, in the rotary tool incorporating the speed reduction mechanism as shown in FIG. 10, the carrier restraining member 10 that restrains the position of the carrier 35 in the axial direction is used to prevent the carrier 35 of the input side transmission unit 3 from falling off. It is necessary to prepare. Therefore, as shown in the drawing, the holding plate 17 constituting the carrier restraining member 10 is arranged at a position where it abuts on the output side end face of the carrier 35.

  However, since the carrier restraining member 10 has such a configuration, the carrier restraining member 10 obstructs the sliding movement of the moving member 40, and the moving member 40 cannot be slid to a position where it contacts the carrier 35. There was a problem. Further, since the carrier restraining member 10 is configured in this way, the carrier restraining member 10 also interferes with the sliding movement of the ring gear 33 of the input side transmission unit 3, and the ring gear 33 exceeds the carrier 35. There was also a problem that it could not slide to the output side to the position.

  Due to these problems, it has been difficult to further reduce the axial dimension of the rotary tool incorporating the reduction mechanism as shown in FIG.

Japanese Patent No. 3911905 JP 2005-288682 A

  The present invention has been invented in view of the above problems, and it is an object of the present invention to reliably prevent the carrier of the input side transmission unit from falling off and to further reduce the axial dimension of the entire speed reduction mechanism. And

  The rotary tool of the present invention capable of solving the above-mentioned problems is an input side comprising a planetary reduction mechanism having a sun gear, a planet gear, a carrier, and a ring gear as a reduction mechanism that transmits the rotational drive of the input shaft to the output shaft. The speed change part and the output side speed change part are connected in series in the axial direction. The input-side transmission unit includes a carrier restraining member that restrains the position of the carrier in the axial direction, and switches between a deceleration state and a non-deceleration state by providing a ring gear slidably in the axial direction. The output side transmission unit switches between a deceleration state and a non-deceleration state by providing a sun gear and a moving member coupled thereto so as to be slidable in the axial direction. The carrier of the input side transmission unit and the moving member are coupled to be slidable in the axial direction. And the said carrier restraint member is arrange | positioned in the part except the area | region pinched in the axial direction by the mutual contact surface of the carrier and moving member of an input side transmission part.

  In the rotary tool of the present invention, the moving member of the output side transmission unit can be slid in the axial direction to a position where it is in close contact with the carrier of the input side transmission unit. Therefore, it is possible to ensure the switching stroke while suppressing the dimension of the entire mechanism in the axial direction while reliably preventing the carrier of the input side transmission unit from falling off.

  In the rotary tool of the present invention, the carrier restraining member is disposed in a portion excluding a region that contacts when the ring gear of the input side transmission portion slides to the output side position beyond the carrier. Is preferred. By doing in this way, it becomes possible to slide the ring gear of the input side transmission unit in the axial direction to a position exceeding the carrier. For this reason, it is possible to ensure the switching stroke while further suppressing the axial dimension of the entire mechanism after reliably preventing the carrier of the input side transmission unit from falling off.

  Moreover, it is also preferable to attach a stopper that comes into contact with the carrier to the tip of the input shaft that protrudes further to the output side than the carrier of the input side shifting portion as the carrier restraining member. By doing in this way, the said carrier restraint member can be made into a lightweight and compact structure.

  Also, a torque transmission member for slidably connecting the carrier of the input side transmission unit and the moving member in the axial direction is provided on the carrier, and a thrust receiving portion that contacts the tip of the torque transmission member is provided as the carrier restraining member. It is also preferable to arrange them. By doing in this way, the said carrier restraint member can be made into a lightweight and compact structure, and the fall of the carrier of an input side transmission part can also be prevented effectively.

  Furthermore, it is preferable that the thrust receiving portion has a rotating disk that rotates integrally with the torque transmission member or a bearing that smoothens the rotation of the torque transmission member. By doing in this way, sliding resistance can be reduced and the fall of power transmission efficiency can be suppressed.

  Moreover, it is also preferable to arrange an elastic member between the carrier of the input side transmission unit and the moving member as the carrier restraining member. By doing so, the carrier restraining member can be easily incorporated and vibrations are also absorbed by the elastic member.

  It is also preferable that the moving member is provided with a meshing portion that meshes with the carrier when it is slid to a position where it contacts the carrier of the input side transmission unit. By doing in this way, the play of the said moving member can be prevented effectively and the loss of transmission efficiency can be prevented.

  Further, it is preferable that a further speed reducing portion that always operates in a decelerating state is connected in series in the axial direction to the input side of the input side transmission portion. As described above, by arranging the speed reduction stage on the side with the higher rotational speed, it is possible to prevent problems such as gear breakage during mode switching.

  Also, it has an impact mode using an impact mechanism consisting of a hammer and anvil, and a drill driver mode that transmits the rotational drive of the input shaft to the output shaft without causing the impact mechanism to function, and slides the moving member in the axial direction. It is further preferable to include a switching means for switching between the impact mode and the drill driver mode. By doing in this way, a reduction ratio change and mode switching can be performed simultaneously by the sliding movement of a moving member, and the enlargement of the whole mechanism is suppressed. In addition, the operation burden is reduced for the user.

  According to the rotary tool of the present invention, it is possible to further reduce the size of the entire speed reduction mechanism in the axial direction while reliably preventing the carrier of the input side transmission unit from falling off. Therefore, it is possible to provide a user-friendly rotary tool. There is an effect that can be done.

It is a sectional side view at the time of drill driver High mode of the rotary tool of the 1st example in the embodiment of the present invention. It is a sectional side view at the time of the drill driver Low mode of the rotary tool same as the above. It is a sectional side view at the time of impact mode of the rotary tool same as the above. It is a sectional side view in the case of drill driver High mode of the rotary tool of the 2nd example in the embodiment of the present invention. It is a sectional side view at the time of drill driver High mode of the rotary tool of the 3rd example in an embodiment of the present invention. It is a sectional side view at the time of the drill driver High mode of the rotary tool of the 4th example in an embodiment of the present invention. It is a sectional side view at the time of the drill driver High mode of the rotary tool of the 5th example in an embodiment of the present invention. It is a sectional side view at the time of impact mode of the rotary tool same as the above. It is a sectional side view at the time of drill driver High mode of the rotary tool of the 6th example in an embodiment of the present invention. It is side sectional drawing at the time of the drill driver High mode of the rotary tool invented previously.

  The present invention will be described based on embodiments shown in the accompanying drawings. The basic configuration of the present invention is the same as that of the rotary tool of FIG. 10 previously invented. Therefore, the structure of the rotary tool shown in FIG. 10 will be described in detail first, and then a characteristic configuration obtained by further improving the present invention will be described in detail based on FIGS.

  The rotary tool shown in FIG. 10 is a multi-impact rotary tool that can freely switch between an impact mode and a drill driver mode. In addition, this multi-impact rotary tool has planetary speed reduction mechanisms in three stages, of which the second and third stage planetary speed reduction mechanisms can be switched between a deceleration state and a non-deceleration state by an external operation. .

  That is, the multi-impact rotary tool switches between an impact mode using the impact mechanism 6 including the hammer 61 and the anvil 91 and a drill driver mode in which the output shaft 9 is rotated without performing an impact operation on the impact mechanism 6. The switching means to be performed can be switched by externally operating the speed change operation unit 14.

  Further, the multi-impact rotary tool transmits the output of the motor 13 to the drive shaft 8 after being decelerated by the multistage reduction mechanism, and from the drive shaft 8 via the impact mechanism 6 (or without the impact mechanism 6). An output is given to the output shaft 9. Hereinafter, the side on which the motor 13 is positioned with respect to the drive shaft 8 will be referred to as “input side”, and the opposite side as “output side”.

  The housing 1 constituting the outer shell of the multi-impact rotary tool has a grip portion 11, and a trigger switch 12, which is an operation switch of the motor 13, is disposed at the base portion of the grip portion 11.

  The impact mechanism 6 includes a drive shaft 8, a hammer 61, an anvil 91, a biasing spring 63 that biases the hammer 61 toward the anvil 91, and a spring receiver 64 that receives the biasing spring 63 on the rear end side. It consists of

  More specifically, in the impact mechanism 6, the steel ball 65 is engaged with the groove-shaped cam provided on the outer periphery of the drive shaft 8 and the groove-shaped cam provided on the inner periphery of the hammer 61 to drive the impact mechanism 6. The hammer 61 can be rotated along with the rotation of the shaft 8. When rotating, the protrusion 62 extending to the output side of the hammer 61 engages the anvil 91 to rotate the anvil 91 and the output shaft 9, and when the torque on the output shaft 9 side increases, While rotating with respect to the drive shaft 8, it is provided so as to retreat against the biasing spring 63 according to the lead of the cam.

  Here, when the protrusion 62 gets over the anvil 91, the hammer 61 advances according to the lead of the cam by the urging of the urging spring 63, and the protrusion 62 strikes the anvil 91 in the rotational direction.

  The first-stage deceleration unit 2 constituting the deceleration mechanism is a planetary deceleration mechanism that always operates in a decelerating state, and the second-stage decelerating unit 3 and the third-stage decelerating unit 5 are in a decelerating state and a non-decelerating state. Is a switchable planetary speed reduction mechanism. Therefore, in the following description, the second-stage reduction unit 3 is referred to as “input-side transmission unit 3”, and the third-stage reduction unit 5 is referred to as “output-side transmission unit 5”. By switching the state of the transmission units 3 and 5, a high speed mode and a medium speed mode in which only one of the transmission units 3 and 5 is in a decelerating state, and a low speed mode in which both the transmission units 3 and 5 are in a decelerating state, The three-speed mode can be changed.

  The speed reduction unit 2 includes a first sun gear 21 fixed to an input shaft 132 that is rotated by a motor 13, a first ring gear 23, and a first planet gear 22 that meshes with the first sun gear 21 and the first ring gear 23. , Is composed. The first ring gear 23 is fixed to the motor mount 131, and the speed reducing unit 2 always operates to decelerate the rotation from the motor 13.

  A first transmission shaft 24 is fixed to the first planet gear 22, and the reduced rotation is transmitted to the first carrier 25 through the first transmission shaft 24. And the 2nd sun gear 31 of the input side transmission part 3 is integrally formed in the drive shaft 8 side of the said 1st carrier 25. As shown in FIG.

  The input side transmission unit 3 includes the second sun gear 31 disposed concentrically with the first sun gear 21 of the speed reduction unit 2, the second ring gear 33 slidably disposed along the axial direction, and the first 2 and a second planet gear 32 that meshes with the second sun gear 31 and the second ring gear 33. A second transmission shaft 34 that transmits torque to the second carrier 35 is fixed to the second planet gear 32. The second carrier 35 is rotatably supported with respect to the input shaft 132 via the bearing 15.

  The second ring gear 33 is slidable along the axial direction so that it can be switched between two positions: an input side position that is a position on the motor 13 side and an output side position that is a position on the drive shaft 8 side. It has become. In the switching operation between the two positions, the input side shift handle 141 constituting the shift operation unit 14 is externally operated, and the second ring gear 33 is slid along the axial direction via a shift spring (not shown). Do that.

  FIG. 10 shows the case where the second ring gear 33 is in the output side position. At this time, the second ring gear 33 meshes with the external teeth 351 formed on the second carrier 35 so as not to be relatively rotatable, and is in a non-decelerated state.

  On the other hand, when the input side shift handle 141 is moved to the input side, the second ring gear 33 moves to the input side position, and the meshing between the external teeth 351 of the second carrier 35 and the second ring gear 33 is released. At the same time, the engaging portion 331 extending in the axial direction of the second ring gear 33 engages with the engaging portion 231 of the first ring gear 23 in a non-rotatable manner. Due to the engagement of both the engaging portions 231 and 331, the second ring gear 33 is held by the first ring gear 23 and cannot be rotated. Thereby, the input side transmission part 3 will be in the deceleration state.

  Further, a holding pin 16 is provided on the output side of the second ring gear 33. The holding pins 16 are used for positioning when the second ring gear 33 is moved to the output side position and for preventing the second ring gear 33 from falling off to the output side.

  Further, a plurality of pin-shaped torque transmission members 41 project from the second carrier 35 toward the output side along the axial direction. A transmission carrier 42 is arranged on the torque transmission member 41 so as to be slidable in the axial direction.

  The transmission carrier 42 is slidable along the axial direction into two positions, an input side position that is a position on the motor 13 side and an output side position that is a position on the drive shaft 8 side. Torque from the second carrier 35 is transmitted to the transmission carrier 42 through the torque transmission member 41 at any position described above. The sliding movement of the transmission carrier 42 is performed via a speed change spring (not shown) by externally operating the output side speed change handle 142 constituting the speed change operation portion 14.

  A third sun gear 51 of the output side transmission unit 5 is integrally formed on the output side of the transmission carrier 42.

  The third sun gear 51 meshes with the third planet gear 52 of the output side transmission unit 5 in a state where the transmission carrier 42 is at the output side position. When the transmission carrier 42 moves to the input side position, the meshing with the third planet gear 52 is released. Therefore, the output side transmission unit 5 switches between deceleration and non-deceleration as the transmission carrier 42 moves.

  The third planet gear 52 includes a large diameter gear portion 521 that meshes with the third sun gear 51 and a small diameter gear portion 522 that has a smaller diameter than the large diameter gear portion 521 and meshes with the third ring gear 53. It is a gear. That is, the output side transmission unit 5 is a speed reduction mechanism called an IV type planet in the 2K-H type planetary speed reduction mechanism.

  The third planet gear 52 is a gear provided with two-stage external teeth in which the small diameter gear portion 522 and the large diameter gear portion 521 are concentric and are not relatively rotatable. A third transmission shaft 54 that transmits drive to the third carrier 55 is attached to the rotation center of the third planet gear 52.

  Further, a clutch mechanism 7 is disposed on the output side of the output side transmission unit 5. The third ring gear 53 is provided with a clutch peak 71 protruding on the output side. The clutch mechanism 7 is a mechanism in which a clutch spring 74 biases a steel ball 72 positioned between clutch peaks 71 via a thrust plate 73. When a torque exceeding a set value is applied, the clutch peak 71 is moved to a steel ball. It functions to push 72 to the output side and cause the third ring gear 53 to idle. Reference numeral 75 denotes a clutch adjustment screw.

  A holding pin 16 is provided on the input side of the third ring gear 53 to prevent the third ring gear 53 from being shifted to the input side by being pushed by the steel ball 72 of the clutch mechanism 7.

  A cylindrical intermediate output shaft 56 is fixed to the output side of the third carrier 55 of the output side transmission unit 5, and torque from the third carrier 55 is transmitted to the intermediate output shaft 56. The front end of the intermediate output shaft 56 is engaged with the rear end of the drive shaft 8 in a relatively non-rotatable manner, and torque is transmitted to the drive shaft 8. The third carrier 55 and the intermediate output shaft 56 may be integrally formed.

  Further, the input side end portion of the connection shaft 43 is fixed to the inner periphery of the transmission carrier 42, and the transmission carrier 42, the connection shaft 43, and the third sun gear 31 are integrally rotated. An output side end portion of the connecting shaft 43 is rotatably inserted into the inner periphery of the intermediate output shaft 56. The connection shaft 43 slides together with the third sun gear 31 as the transmission carrier 42 slides. That is, the transmission carrier 42 and the connecting shaft 43 form a moving member 40 that is connected to the third sun gear 31 and rotates and slides integrally.

  An intermediate shaft direct connection portion 431 is formed on the outer peripheral surface of the output side end portion of the connecting shaft 43. This intermediate shaft direct connection portion 431 can be engaged with a direct connection engagement portion 561 provided on the inner peripheral input side of the intermediate output shaft 56 in a non-rotatable manner. However, the engagement between the intermediate shaft direct coupling portion 431 and the direct coupling engaging portion 561 is such that the transmission carrier 42 moves from the output side position to the input side position and the third sun gear 51 releases the mesh with the third planet gear 52. It is done only in the state.

  When the intermediate shaft direct connection portion 431 and the direct connection engagement portion 561 are engaged, the transmission carrier 42 directly transmits torque to the intermediate output shaft 56 without passing through the output side transmission portion 5. In the engaged state, the output-side transmission unit 5 is in a non-decelerated state and is in a non-use state where torque is not transmitted, and the clutch mechanism 7 is invalidated.

  When the transmission carrier 42 returns to the output side position shown in FIG. 10 by an external operation of the output side shift handle 142, the engagement between the intermediate shaft direct connection portion 431 and the direct connection engagement portion 561 is released. At this time, the third sun gear 51 meshes with the third planet gear 52, the output side transmission unit 5 is decelerated, and the clutch mechanism 7 is activated.

  In the space S in which the transmission carrier 42 slides, holding plates 17 are provided at the end positions on the input side and the output side. Among these, the input side holding plate 17 constitutes the carrier restraining member 10 for preventing the second carrier 35 included in the input side transmission unit 3 from falling off. The holding pin 16 on the output side of the second ring gear 33 positions the holding plate 17. The output-side holding plate 17 is for preventing the third planet gear 52 included in the output-side transmission unit 5 from falling off.

  The drive shaft 8 to which torque is transmitted from the intermediate output shaft 56 is provided with a switching pin 45 so as to be rotatable and slidable in the axial direction in a through hole formed so that both ends in the axial direction are opened. doing. At the output side end of the switching pin 45, switching means comprising a connecting member 44 for mode switching is provided to be rotatable and immovable in the axial direction.

  The connecting member 44 is non-rotatable and slidable in the axial direction with respect to the drive shaft side engaging portion 81 formed in the through hole of the drive shaft 8 and the anvil side engaging portion 92 formed in the anvil 91. Can be engaged. The engaging portions 81 and 92 themselves rotate relative to each other without directly interfering with each other, but are connected to rotate integrally when the connecting member 44 is interposed.

  That is, when the connecting member 44 is engaged with both the drive shaft side engaging portion 81 and the anvil side engaging portion 92, the engaging portions 81 and 92 are held by the connecting member 44 so as not to be relatively rotatable. 8 and anvil 91 are connected. Then, when the coupling member 44 releases the engagement with one of the engaging portions 81 and 92, the structure returns to the state in which the relative rotation is possible again.

  The input side end of the switching pin 45 is press-fitted into the inner periphery of the connecting shaft 43. Therefore, the switching pin 45 rotates together with the transmission carrier 42 via the connecting shaft 43 and slides together with the transmission carrier 42 sliding.

  Then, the sliding of the switching pin 45 causes the connecting member 44 to engage only with the drive shaft side engaging portion 81 without engaging with the anvil side engaging portion 92, and with the drive shaft side engaging portion 81 and the anvil. The state is switched to a state of engaging both of the side engaging portions 92.

  In a state in which the connecting member 44 engages only with the drive shaft side engaging portion 81, both the engaging portions 81 and 92 can be rotated relative to each other, and the torque transmitted to the drive shaft 8 is transmitted via the impact mechanism 6 to the anvil 91. And the impact mode is transmitted to the output shaft 9. Further, in a state where the connecting member 44 is engaged with both the engaging portions 81 and 92, the drive shaft 8 and the anvil 91 are connected so as not to rotate relative to each other, and the torque of the drive shaft 8 is not affected by the impact mechanism 6. The drill driver mode is transmitted directly to the output shaft 9.

  The state shown in FIG. 10 is a state where both the input side shift handle 141 and the output side shift handle 142 are slid to the output side. At this time, in the input side transmission unit 3, the second ring gear 33 is at the output side position and is in a non-decelerated state. Moreover, in the output side transmission part 5, since the transmission carrier 42 exists in an output side position and it will be in a deceleration state, since the connection member 44 engages both the engaging parts 81 and 92, it will be in a drill driver mode.

  On the other hand, although not shown, for example, when only the input side shift handle 141 is slid to the input side, the input side transmission unit 3 is switched to the decelerating state, and all the planetary decelerating mechanisms are set to the lowest speed mode in the decelerating state. At this time, since the transmission carrier 42 is in the output side position, it is in the drill driver mode.

  Further, although not shown in the drawing, when the output side speed change handle 142 is further slid to the input side, the output side speed change unit 5 is switched to the non-decelerating state by the sliding movement of the transmission carrier 42 to the input side position. Is switched to the impact mode in which only the drive shaft side engaging portion 81 is engaged.

  In the multi-impact rotary tool, since the input side transmission unit 3 is set to have a smaller reduction ratio than the output side transmission unit 5, the impact mode is more effective than the drill driver high mode (the mode shown in FIG. 10). Is in high-speed mode. Conversely, if the input side transmission unit 3 is set to have a larger reduction ratio than the output side transmission unit 5, the impact mode becomes the low speed mode rather than the drill driver high mode.

  The configuration of the rotary tool shown in FIG. 10 has been described above. In the following, the rotary tool of the present invention obtained by further improving the rotary tool will be described. In addition, about the structure similar to the rotary tool shown in FIG. 10, the code | symbol and detailed description in drawing are partially abbreviate | omitted, and only the characteristic structure (improved part) different from this rotary tool is explained in full detail below. .

  1 to 3 show a first example of a rotary tool in an embodiment of the present invention. The rotary tool of the first example is a multi-impact rotary tool similar to the rotary tool of FIG. 10, and FIG. 1 shows a case in the drill driver high mode similar to FIG. 10. FIG. 2 shows a case in the drill driver low mode, and FIG. 3 shows a case in the impact mode.

  In the drill driver high mode shown in FIG. 1, both the input side shift handle 141 and the output side shift handle 142 are at the output side position, the input side transmission unit 3 is in the non-deceleration state, and the output side transmission unit 5 is in the deceleration state. Drill driver mode. In the drill driver low mode shown in FIG. 2, the input side transmission handle 141 is in the input side position and the output side transmission handle 142 is in the output side position, and both the input side transmission unit 3 and the output side transmission unit 5 are in the decelerating state. Drill driver mode. The impact mode shown in FIG. 3 is an impact mode in which both the input side transmission handle 141 and the output side transmission handle 142 are at the input side position, the input side transmission unit 3 is in a deceleration state, and the output side transmission unit 5 is in a non-deceleration state. It is.

  In the rotary tool of the first example, the carrier restraint member 10 that restrains the position in the axial direction of the second carrier 35 that constitutes the input-side transmission unit 3 is used in the space S as in the rotary tool of FIG. The holding plate 17 is not disposed so as to partition the outer peripheral side in the axial direction, but a stopper 101 that is a C-shaped ring member is attached and fixed to the distal end portion of the input shaft 132. A concave groove is formed along the circumferential direction on the outer peripheral surface of the output side of the input shaft 132, and the stopper 101 is fixed to the input shaft 132 by being fitted in the concave groove.

  The input shaft 132 is provided such that its tip protrudes to the output side from the second carrier 35 of the input-side transmission unit 3, and the C-shaped input of the stopper 101 attached to the tip is provided. Since the side end surface is locked to the output side end surface of the second carrier 35, the second carrier 35 is prevented from falling off to the output side (space S side).

  Further, the connecting shaft 43 fixed to the inner periphery of the transmission carrier 42 is provided with a recess 432 into which the tip of the input shaft 132 and the stopper 101 can be inserted in a portion facing the input shaft 132 in the axial direction. Provided. The recess 432 has a circular cross section that is slightly larger in diameter than the stopper 101.

  With the above configuration, in the rotary tool of the first example, the location where the carrier restraint member 10 formed of the stopper 101 is disposed is brought into contact with the second carrier 35 and the transmission carrier 42 of the input-side transmission unit 3. They are arranged in a portion excluding a region sandwiched between the surfaces 352 and 421 in the axial direction.

  Therefore, when the transmission carrier 42 slides to the input side and switches to the impact mode shown in FIG. 3, the tip end portion of the input shaft 132 and the stopper 101 are immersed in the recess 432 of the connecting shaft 43, and the input side transmission portion The third second carrier 35 and the transmission carrier 42 are in close contact with each other at their contact surfaces 352 and 421.

  That is, since the stopper 101 is not in the way and the transmission carrier 42 can be slid to the input side until it comes into close contact with the second carrier 35, the axial dimension of the entire mechanism is suppressed, It is possible to ensure a switching stroke.

  In addition, since the rotary tool of the first example has the above-described configuration, the second ring gear 33 of the input-side transmission unit 3 exceeds the second carrier 35 in the arrangement position of the carrier restraint member 10 including the stopper 101. It is also a portion excluding the area that comes into contact when sliding to the output side position.

  Therefore, when in the drill driver high mode shown in FIG. 1, the stopper 101 does not get in the way, and the second ring gear 33 slides to a position where its output side tip exceeds the output side end surface of the carrier 35. it can. This also secures the switching stroke while suppressing the axial dimension of the entire mechanism.

  Next, the rotary tool of the 2nd example in embodiment of this invention is demonstrated based on FIG. FIG. 4 shows the drill driver high mode. Detailed description of the same configuration as that of the rotary tool shown in FIG. 10 and the rotary tool of the first example will be omitted, and only the characteristic configuration will be described in detail below.

  In the rotary tool of the second example, an annular plate that contacts the output side end face of the torque transmission member 41 as the carrier restraint member 10 that restrains the axial position of the second carrier 35 of the input side transmission unit 3. A cylindrical thrust receiving portion 102 is disposed. As described above, the torque transmission member 41 is a pin-like member for slidably connecting the second carrier 35 and the transmission carrier 42 of the input side transmission unit 3 in the axial direction, and the input side end portion thereof is The output carrier end is fixed to the second carrier 35, and is slidably passed through a connecting hole 422 that penetrates the transmission carrier 42 in the axial direction.

  The thrust receiving portion 102 also serves as the holding plate 17 that prevents the third planet gear 52 included in the output-side transmission portion 5 from dropping off. That is, the partition plate-like thrust receiving portion 102 is disposed at the output side end portion of the space S (the space between the second carrier 35 and the third planet gear 52) in which the transmission carrier 42 slides, and its annular shape. The output-side end surface of the torque transmission member 41 is brought into contact with the smooth input-side end surface, and the input-side end surface of the third planet gear 52 is brought into contact with the output-side end surface that also forms an annular shape. The output side end surface of the torque transmitting member 41 slides smoothly with respect to the input side end surface of the thrust receiving portion 102.

  In the rotary tool of the second example, by providing the above-described configuration, the arrangement position of the carrier restraint member 10 including the thrust receiving portion 102 is set so that the carrier 35 and the transmission carrier 42 of the input side transmission portion 3 are in contact with each other. Except for the region sandwiched in the axial direction by 352, 421 and the region that contacts when the second ring gear 33 of the input side transmission unit 3 slides to the output side position beyond the second carrier 35. It is arranged. Therefore, the transmission carrier 42 can slide to a position where it is in close contact with the second carrier 35 without the thrust receiving portion 102 being in the way, and the second ring gear 33 can be slid into the second carrier 35 as shown in FIG. It is possible to slide to a position exceeding. Therefore, it is possible to ensure the switching stroke while suppressing the axial dimension of the entire mechanism.

  Although not shown, when the transmission carrier 42 slides to the input side and switches to the impact mode, the tip of the input shaft 132 is immersed in the recess 432 of the connecting shaft 43, and the carrier 35 of the input side transmission unit 3. Needless to say, the transmission carrier 42 can be closely attached.

  An annular guide groove in which the tip of the torque transmission member 41 is slidably disposed may be formed on the input side end surface of the thrust receiving portion 102. If the guide groove is formed, the sliding of the torque transmission member 41 is further smoothed.

  Next, the rotary tool of the 3rd example in the embodiment of the present invention is explained based on FIG. FIG. 5 shows a drill driver high mode. Since the rotary tool of the third example is based on the rotary tool of the second example, detailed description of the same configuration as the second example is omitted, and only the configuration different from the second example is described below. Detailed description.

  In the rotary tool of the third example, the thrust receiving portion 102 that constitutes the carrier restraining member 10 includes an annular thin plate-like holding plate 17, an annular turntable 103 that rotates integrally with the torque transmission member 41, and It is formed with. The holding plate 17 and the turntable 103 are arranged in close contact with each other so that their opposing surfaces are slidable. The holding plate 17 abuts the input side end surface of the third planet gear 52 on the output side end surface. To prevent falling off. Further, the rotary disk 103 has a circular concave groove on the input side end surface thereof, and the output side tip portion of the columnar torque transmission member 41 is fitted in the concave groove.

  The turntable 103 is rotationally driven integrally with the torque transmission member 41 and the transmission carrier 42 while being in sliding contact with the holding plate 17 in the circumferential direction. In the thrust receiving portion 102 having the rotating disk 103, the second carrier 35 can be prevented from dropping through the torque transmitting member 41 while ensuring smooth rotation. In addition, the transmission carrier 42 can be effectively prevented from falling.

  In the third example, the input shaft 132 is formed shorter than in the case of the first example, and the inner diameter of the second carrier 35 and the like is further increased, thereby further reducing the weight of the entire mechanism. The weight reduction is possible because the fastener 101 as in the first example is not used as the carrier restraining member 10.

  Next, the rotating tool of the 4th example in the embodiment of the present invention is explained based on FIG. FIG. 6 shows a drill driver high mode. Note that the rotating tool of the fourth example is based on the rotating tool of the second example as in the third example. Therefore, detailed description of the same configuration as the second example is omitted, and only the configuration different from the second example is described in detail below.

  In the rotary tool of the fourth example, the thrust receiving portion 102 constituting the carrier restraining member 10 is formed by an annular thin plate-like holding plate 17 and a bearing 104 that is closely fixed to the holding plate 17. The bearing 104 is an annular thrust bearing, and is arranged so that the output side end surface of the torque transmission member 41 is pressed against the input side end surface. A roller bearing is preferably used as the bearing 104.

  In the thrust receiving portion 102 having the bearing 104, the second carrier 35 can be prevented from falling off via the torque transmission member 41 while ensuring smooth rotation. In addition, the transmission carrier 42 can be effectively prevented from falling.

  The thrust receiving portion 102 may be formed by combining the bearing 104 and the third example rotating disk 103. In this case, for example, the bearing 104 is disposed between the rotating disk 103 and the holding plate 17.

  Next, the rotary tool of the 5th example in an embodiment of the present invention is explained based on Drawing 7 and Drawing 8. FIG. 7 shows the drill driver high mode, and FIG. 8 shows the impact mode. Detailed description of the same configuration as that of the rotary tool shown in FIG. 10 and the rotary tool of the first example will be omitted, and only the characteristic configuration will be described in detail below.

  In the rotary tool of the fifth example, the carrier restraining member 10 that prevents the second carrier 35 from falling off is formed of a compression coil spring at the axial center portion of the space S in which the transmission carrier 42 and the connecting shaft 43 slide. An elastic member 105 is disposed.

  In the fifth example, as in the first example, the tip end of the input shaft 132 is provided so as to protrude to the output side from the second carrier 35, and the portion of the connecting shaft 43 that faces the tip of the input shaft 132 is provided. Is provided with a recess 432 into which the tip of the input shaft 132 can be immersed. The recess 432 has a circular cross section that is slightly larger in diameter than the coiled elastic member 105.

  Then, the input side end portion of the coiled elastic member 105 is fitted to the protruding portion of the input shaft 132 from the second carrier 35, and the output side end portion of the elastic member 105 is connected to the recess 432 of the connecting shaft 43. It is placed inside.

  Therefore, when the transmission carrier 42 slides to the input side and switches to the impact mode shown in FIG. 8, the elastic member 105 is compressed in the axial direction, and the tip end of the input shaft 132 is immersed in the recess 432 of the connecting shaft 43. Then, the carrier 35 and the transmission carrier 42 of the input side transmission unit 3 are in close contact with each other at the contact surfaces 352 and 421. At this time, the entire elastic member 105 in the maximum compressed state is immersed in the recess 432. In the impact mode, the transmission carrier 42 receives an urging force toward the output side by the elastic member 105, but the transmission carrier 42 is restrained by a speed change spring (not shown), so that its position is maintained without any problem.

  In the rotary tool of the fifth example having the above-described configuration, the location where the carrier restraining member 10 made of the elastic member 105 is arranged by the contact surfaces 352 and 421 of the carrier 35 and the transmission carrier 42 of the input side transmission unit 3. It is arranged in a portion excluding the region sandwiched in the axial direction and the region that contacts when the second ring gear 33 of the input side transmission unit 3 slides to the output side position beyond the second carrier 35. . Therefore, the transmission carrier 42 can be slid to a position (see FIG. 8) in close contact with the second carrier 35 without the elastic member 105 getting in the way. Further, the second ring gear 33 can slide to a position exceeding the second carrier 35 (see FIG. 7). Therefore, it is possible to ensure the switching stroke while suppressing the axial dimension of the entire mechanism.

  Next, a sixth example of the rotary tool according to the embodiment of the present invention will be described with reference to FIG. FIG. 9 shows the impact mode. In addition, since the rotary tool of the sixth example is based on the rotary tool of the first example, detailed description of the same configuration as the first example is omitted, and only the configuration different from the first example is described. This will be described in detail below.

  In the rotary tool of the sixth example, when the transmission carrier 42 is slid to the position where it contacts the second carrier 35 of the input side transmission unit 3 and switched to the impact mode, the external teeth of the second carrier 35 A meshing portion 423 that meshes with 351 is provided. The meshing portion 423 is provided so as to project in a tooth shape from the outer peripheral portion of the transmission carrier 42 toward the input side, and has a structure that does not mesh with the external teeth 351 of the second carrier 35 except in the impact mode.

  In other words, the external teeth 351 of the second carrier 35 mesh with the second ring gear 33 slid to the output side in the drill driver high mode so as not to rotate relative to each other, and the transmission slid to the input side in the impact mode. The carrier 42 meshes with the meshing portion 423 of the carrier 42 so as not to be relatively rotatable. For this reason, when in the impact mode, the transmission carrier 42 is not rattled by the impact generated by the impact mechanism 6 and the transmission loss is reduced.

  In addition, an overlap portion 424 that protrudes toward the input side is provided on the outer peripheral portion of the transmission carrier 42. The overlap portion 424 is formed so as to cover at least a part of the outer periphery side of the second carrier 35 when in the impact mode in which the second carrier 35 and the transmission carrier 42 of the input side transmission portion 3 are in close contact with each other. . The overlap portion 424 is provided, so that a dimension for forming the grooved transmission spring engaging portion 425 on the outer peripheral surface of the transmission carrier 42 is secured, and the shaft is formed in the other portion of the transmission carrier 42. The thickness in the direction can be made as thin as possible. Therefore, it is possible to further suppress the axial dimension of the entire mechanism.

  Needless to say, the above-mentioned configuration characteristically provided in the sixth example may be further adopted in the rotary tools of the second to fifth examples.

  In the above, the rotary tool of the 1st example-the 6th example was demonstrated. In any rotary tool, the input side transmission unit 3 and the output side transmission unit 5 are connected in series in the axial direction, and the input side transmission unit 3 further operates in a decelerating state on the input side. The speed reduction part 2 is connected in series in the axial direction. The speed reduction unit 2 is a speed reduction stage that directly receives the torque from the motor 13 and has a high rotational speed. By making this a speed reduction stage that does not shift gears, problems such as gear breakage occur at the time of mode switching. It is preventing.

  Each rotary tool has an impact mode using the impact mechanism 6 and a drill driver mode that transmits the rotational drive of the input shaft 132 to the output shaft 9 without causing the impact mechanism 6 to function. There is provided switching means for switching between the impact mode and the drill driver mode as the moving member 40 including the carrier 42 and the connecting shaft 43 slides in the axial direction. Therefore, the mode change can be performed at the same time as the reduction ratio is changed by the sliding movement of the moving member 40, the enlargement of the entire mechanism is suppressed, and the change of the reduction ratio and the mode change are performed as separate operations for the user. There is no need, and there is an advantage that the burden of handle operation is reduced. The number of gear positions to be provided is not limited to two, and three or more gear stages may be provided to set the impact mode to the second speed or higher, or the drill driver mode to the third speed or higher.

  The present invention has been described above based on the embodiments shown in the accompanying drawings. However, the present invention is not limited to the embodiments of the above-described examples, and may be appropriately used in each example as long as it is within the intended scope of the present invention. It is possible to change the design of the above and to apply a combination of the configurations of the examples as appropriate.

132 Input shaft 2 Deceleration unit 21 First sun gear 22 First planet gear 23 First ring gear 25 First carrier 3 Input side transmission unit 31 Second sun gear 32 Second planet gear 33 Second ring gear 35 Second carrier 352 Contact Surface 40 Moving member 41 Torque transmission member 42 Transmission carrier 421 Contact surface 423 Engagement portion 43 Connection shaft 44 Connection member 5 Output side transmission portion 51 Third sun gear 52 Third planet gear 521 Large diameter gear portion 522 Small diameter gear portion 53 Third Ring gear 55 Third carrier 6 Impact mechanism 8 Drive shaft 10 Carrier restraining member 101 Fastener 102 Thrust receiving portion 103 Rotary disc 104 Bearing 105 Elastic member

Claims (10)

  As a speed reduction mechanism that transmits the rotational drive of the input shaft to the output shaft, an input side transmission unit and an output side transmission unit composed of a planetary reduction mechanism having a sun gear, a planet gear, a carrier, and a ring gear are connected in series in the axial direction. The input side transmission unit includes a carrier restraining member that restrains the position of the carrier in the axial direction, and switches between a deceleration state and a non-deceleration state by providing a ring gear slidably in the axial direction. The output-side transmission unit switches between a deceleration state and a non-deceleration state by providing a sun gear and a moving member connected to the sun gear so as to be slidable in the axial direction. The rotary tool is configured to be slidably connected in the axial direction, and the carrier restraining member is formed on the contact surface between the carrier and the moving member of the input side transmission unit. Rotary tool, characterized in that is disposed in the portion excluding the region between axially I. The said carrier restraint member is arrange | positioned in the part except the area | region which contacts, when the ring gear of an input side transmission part slides to the position of the output side exceeding a carrier. Rotating tool.   3. The stopper according to claim 1, wherein a stopper that contacts the carrier is attached to the tip of the input shaft that protrudes further to the output side than the carrier of the input side transmission unit as the carrier restraining member. Rotary tool.   A torque transmission member for slidably connecting the carrier of the input side transmission unit and the moving member in the axial direction is provided on the carrier, and a thrust receiving portion that contacts the tip of the torque transmission member is disposed as the carrier restraining member. The rotary tool according to claim 1 or 2, wherein   The rotary tool according to claim 4, wherein the thrust receiving portion includes a rotary disk that rotates integrally with the torque transmission member.   The rotary tool according to claim 4, wherein the thrust receiving portion includes a bearing that facilitates rotation of the torque transmission member.   The rotary tool according to claim 1 or 2, wherein an elastic member is disposed between the carrier of the input side transmission unit and the moving member as the carrier restraining member.   The rotating tool according to any one of claims 1 to 7, wherein the moving member is provided with a meshing portion that meshes with the carrier when the movable member slides to a position where it contacts the carrier of the input side transmission unit.   The rotary tool according to any one of claims 1 to 8, wherein a speed reduction portion that always operates in a speed reduction state is connected in series in the axial direction on the input side of the input side transmission portion. It has an impact mode that uses an impact mechanism consisting of a hammer and anvil, and a drill driver mode that transmits the rotational drive of the input shaft to the output shaft without causing the impact mechanism to function. The rotary tool according to any one of claims 1 to 9, further comprising switching means for switching between the impact mode and the drill driver mode.

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