JP5118602B2 - Rotating power equipment - Google Patents

Description

  The present invention relates to a rotary power device capable of changing the meshing of gears.

  Patent Document 1 describes a rotary power device having a planetary gear mechanism. In this rotary power device, a carrier (drive gear) having a large number of teeth in the circumferential direction, a ring gear (meshing gear) having a large number of teeth in the circumferential direction, and a carrier are rotatably supported. By providing planet gears in multiple stages, a multi-stage planetary gear mechanism is formed. The ring gear is slidable in the axial direction, and the reduction ratio can be changed by switching between a position where the teeth of the carrier and the ring gear mesh with each other and a position where they do not mesh. FIG. 16 shows a general shape of the carrier 5 and the ring gear 7 described above.

In such a rotary power device, the ring gear 7 is slid in the direction of the arrow s in FIG. 16 during operation (that is, while the carrier 5 is rotating in the direction of the arrow r in FIG. 16). When trying to mesh, the tooth portions 4 and 6 may not mesh well and switching of the reduction ratio may fail.
Japanese Unexamined Patent Publication No. 63-101545

  This invention is invented in view of the said problem, Comprising: It makes it a subject to provide the rotational power apparatus which can switch a reduction ratio smoothly even if it is driving | running.

The rotational power device of the present invention that solves the above problem rotates the drive gear A having a large number of teeth 4 in the circumferential direction, the meshing gear B having a large number of teeth 6 in the circumferential direction, and the drive gear A. And a motor 1 to be driven. In the rotary power device according to the present invention, the meshing gear B or the driving gear A is slid along the rotational axis direction of the driving gear A, whereby the tooth portions 4 of the driving gear A and the meshing gear B are arranged. The position where 6 is meshed and the position where it is not meshed can be switched freely. In the rotational power device of the present invention, the drive gear A has a large number so that only one or a plurality of teeth 4b, 6b positioned in the circumferential direction in the meshing start region P are meshed with each other. Tooth part 4a of tooth part 4 and tooth part 6a of tooth part 6a of many tooth parts 6 which meshing gear B has in a notch shape, and a tooth which does not have a notch shape In the portions 4b and 6b, a convex curved taper surface 12 is formed at the corner portion of the sliding direction s end portion in the meshing start region P, and the gear portion 6a provided in the cutout shape of the meshing gear B Forms a concave curved tapered surface 13 that connects the end surface of the notch 10 portion and the end surface of the meshing gear B.

By doing in this way, when it is going to mesh | engage the drive gear A and the meshing gear B, it can mesh | engage smoothly only by the tooth | gear parts 4b and 6b which are located apart. Therefore, even when the drive gear A is rotating, the reduction gear ratio can be easily changed by engaging the meshing gear B with the gear. Further, it is further prevented that the tooth portions 4b, 6b not provided with the notch shape collide with each other and fail to mesh.

In rotational power device of the present invention, the shape-outs on SL clipper mesh fit gear B has a shape formed by cutting the sliding direction s end side of the tooth portion 6a, the notch shape of the driving gear A is teeth 4a The shape is preferably cut out over the entire area in the sliding direction s. By doing in this way, weight reduction and cost reduction of the whole gear mechanism can be achieved.

  On the other hand, in the rotary power device of the present invention, it is also preferable that both the cutout shapes of the drive gear A and the meshing gear B are cut out at one end side in the sliding direction s of the tooth portions 4a and 6a. By doing so, when the drive gear A and the meshing gear B are meshed deeply, meshing occurs even in the portions where the notches of the mutual tooth portions 4a and 6a are not provided, and the gears are securely connected. Become so.

  The drive gear A according to the present invention is the carrier 5, the meshing gear B is the slidable ring gear 7, and the planet gear 8 that is rotatably supported by the carrier 5 is further provided. It is also preferable to form the planetary gear mechanism 3 whose ratio can be changed. In this case, it is easy to change the reduction ratio by sliding the ring gear 7 even during operation.

  On the other hand, the drive gear A and the meshing gear B of the present invention are both spur gears 20 and 21, and it is also preferable that the reduction ratio can be changed by switching the power transmission between the spur gears 20 and 21. . In this case, it is easy to change the reduction ratio by sliding the spur gears 20, 21 even during operation.

According to the first aspect of the present invention, some of the tooth portions of the drive gear and the meshing gear can be meshed with each other smoothly, and therefore the reduction ratio can be smoothly achieved even during operation. There is an effect that it can be switched. Further, there is an effect that the driving gear and the meshing gear can be meshed more smoothly.

  In addition to the effect of the invention according to claim 1, the invention according to claim 2 has the effect that the entire gear mechanism can be reduced in weight and cost.

  In addition to the effect of the invention according to claim 1, the invention according to claim 3 is capable of reliably fitting all the tooth portions when the drive gear and the meshing gear are engaged further deeply. There is an effect.

In addition to the effect of the invention according to any one of claims 1 to 3 , the invention according to claim 4 facilitates the reduction ratio of the planetary reduction mechanism by sliding the ring gear even during operation. There is an effect that it can be changed to.

In addition to the effect of the invention according to any one of claims 1 to 3 , the invention according to claim 5 can easily change the reduction ratio by sliding the spur gear even during operation. There is an effect that can be done.

  The present invention will be described based on embodiments shown in the accompanying drawings. An example of the rotary power device according to the embodiment of the present invention is an electric drill driver as shown in FIG. As long as the reduction ratio from the motor 1 to the output shaft 2 can be changed, the same configuration can be applied to other devices such as an electric circular saw.

  An example of a rotary power device that is an electric drill driver has an outer shape composed of a cylindrical main body housing 100 and a handle 101 extending laterally from the main body housing 100. Housed in the main body housing 100 are a motor 1 as a power source and a planetary speed reducing mechanism 3 that reduces the rotational power of the motor 1 and transmits it to the output shaft 2 side.

  6 and 7 show the planetary speed reduction mechanism 3. The planetary reduction mechanism 3 includes a carrier 5, a ring gear 7 having a large number of teeth 6 in the circumferential direction, and a plurality of planet gears 8 that are rotatably supported by the carrier 5 in three stages in a gear box 14. It is prepared for. The tooth portion 6 of the ring gear 7 protrudes inward from the inner peripheral surface thereof. Further, the tooth portion 4 protrudes outward from the outer circumference of the second-stage carrier 5.

  The plurality of first-stage planetary gears 8 mesh between the sun gear 9 that is rotationally driven by the motor 1 and the first-stage ring gear 7. The plurality of second-stage planetary gears 8 mesh between the first-stage carrier 5 and the second-stage ring gear 7. The plurality of third-stage planetary gears 8 mesh between the second-stage carrier 5 and the third-stage ring gear 7. A third-stage carrier 5 that rotatably supports a plurality of third-stage planet gears 8 transmits rotational power to the output shaft 2 side.

Of the ring gears 7 formed in three stages in the planetary reduction mechanism 3, the first and third stage ring gears 7 are fixed to the gear box 14, and the second stage ring gear 7 is connected to the gear box 14. It is slidably provided inside. The second-stage ring gear 7 is slidable along the rotation axis direction of the carrier 5, and when it is located on the left side in the figure, the second-stage carrier 5 and the tooth portions 4, 6 can mesh with each other. Rather, when positioned on the right side in the figure, the second-stage carrier 5 and the teeth 4 and 6 are engaged with each other.

  The ring gear 7 is slid through a lever 15 protruding outward through the opening of the gear box 14, and does not inhibit the rotation of the carrier 5 at the left position in the figure, and the carrier 5 at the right position in the figure. The rotation of the carrier 5 is prohibited when the carrier 5 is engaged. Instead of slidably providing the second-stage ring gear 7, the first-stage or third-stage ring gear 7 may be slidably provided. In this case, the rotation of the first-stage or third-stage carrier 5 is selectively prohibited.

  Next, configurations of the second stage carrier 5 and the ring gear 7 which are characteristic portions of the example will be described in detail with reference to FIGS. The second-stage carrier 5 is a drive gear A in one example, and the second-stage ring gear 7 is a meshing gear B in one example.

  FIG. 1 shows the carrier 5 and the ring gear 7, and FIG. 2 shows an enlarged part of the ring gear 7. As shown in the figure, a notch 10 is provided in the tooth portion 6 that is positioned in a skipped manner among the many tooth portions 6 that the ring gear 7 has in the circumferential direction. That is, in the ring gear 7 as an example, the tooth part 6 provided with the notch 10 (hereinafter referred to as “tooth part 6a”) and the tooth part 6 provided with no notch 10 (hereinafter referred to as “tooth part 6b”). Are alternately arranged in the circumferential direction on the inner peripheral surface of the ring gear 7.

  The notch 10 provided in the tooth portion 6a on the ring gear 7 side has a shape in which the one end side in the sliding direction s of the tooth portion 6a is cut out so as not to be engaged here. This sliding direction s is a direction in which the ring gear 7 slides. Further, one end side in the sliding direction s is a side where the carrier 5 is positioned with respect to the ring gear 7. In other words, a region on the side where meshing with the carrier 5 begins to occur (hereinafter referred to as “meshing start region P”). ").

  Moreover, the notch 11 is provided also in the tooth | gear part 4a located in the circumferential direction among the many tooth | gear parts 4 which the carrier 5 has in the circumferential direction. However, the notch 11 has a shape in which the tooth portion 4a is not cut across the entire region of the tooth portion 4a instead of one end side in the sliding direction s so as not to cause meshing. Accordingly, the tooth portion 4a positioned in a single portion is omitted so as not to mesh, and only the tooth portion 4b without the notch 11 is protruded.

  In this description, the number of teeth when the carrier 5 and the tooth portions 4 and 6 of the ring gear 7 mesh with each other on a one-to-one basis is used as a reference. Therefore, the state in which the tooth portion 4 is omitted means a state that can be interpreted as being omitted when the number of teeth of 1: 1 is used as a reference.

  4 schematically shows a developed sectional view taken along the line XX of FIG. 3, and the manner in which the tooth portions 4 and 6 mesh with each other as the ring gear 7 slides is shown in FIGS. It is shown in the order of b) and (c). As shown in the drawing, there is no tooth portion 4 (4a) on the rotating carrier 5 side, and one tooth portion 6b has a notch 10 on the ring gear 7 side. Therefore, the tooth portion 4 on the carrier 5 side easily passes through the tooth portion 6a and easily engages with the tooth portion 6b by the level difference h between the tooth portion 6a and the tooth portion 6b of the ring gear 7 (particularly, (Refer FIG.4 (b), (c)).

  Further, in the tooth portion 6b where the notch 10 is not provided, a tapered surface 12 is formed at a corner portion at the end in the sliding direction s in the meshing start region P. The tapered surface 12 is formed at a ridge line portion between the triangular end surface formed at the end of the tooth portion 6b in the sliding direction s and the side surface of the tooth portion 6b facing the rotation direction r of the carrier 5. Yes (see FIG. 2). The provision of the tapered surface 12 prevents the tooth portion 4 (4b) of the carrier 5 from hitting the end portion of the tooth portion 6b and failing when engaging.

  In addition, this taper surface 12 may be provided not only on one ridge line at the end of the tooth portion 6b but also on both ridge lines as shown in the modified examples of FIGS. 5 (a) and 5 (b). When both are provided, the failure at the time of meshing can be prevented by providing the tapered surface 12 regardless of whether the carrier 5 rotates forward or backward. The tapered surface 12 may be inclined linearly or may be formed in a convex curved shape.

  Further, in the tooth portion 6a cut out at one end side in the sliding direction s, a concave curved taper surface 13 is formed to connect the end face of the cutout 10 portion and the end face of the ring gear 7 (see FIG. 2). . By providing the tapered surface 13, the strength is enhanced.

  In the example rotary power device having the above-described configuration, for example, the ring gear 7 that was in a position where the meshing is not initially engaged (see FIG. 6A) is slid to the carrier 5 side. Then, first, in the meshing start region P of the ring gear 7, the tooth portion 6 b arranged in the ring gear 7 in the circumferential direction and the tooth portion 4 b arranged in the carrier 5 in the circumferential direction in a row. Will mesh smoothly (see FIG. 6B).

  When the teeth 4b and 6b mesh with each other in the meshing start region P of the ring gear 7, the rotation of the carrier 5 is prohibited here, and the carrier 5 further moves in the sliding direction s while maintaining the positional relationship in the rotational direction r. And slide. That is, when it is slid to the position shown in FIG. 6C beyond the meshing start region P, the carrier 5 and the ring gear 7 are reliably meshed in a large area.

  In the example, in the carrier 5 and the ring gear 7, the tooth portions 4a and 6a with the notches 10 and 11 and the tooth portions 4b and 6b without the notches are alternately provided one by one. , 11 may be continued in the circumferential direction. That is, a plurality of tooth portions 4 a and 6 a having notches 10 and 11 and a single tooth portion 4 b and 6 b without notches may be alternately arranged in the circumferential direction in the carrier 5 and the ring gear 7. In this case, the number of consecutive tooth portions 4a and the number of consecutive tooth portions 6a are matched. Further, in the example, the ring gear 7 side is slidable, but the carrier 5 side may be slid.

  Further, in the example, the tooth portion 6a on the ring gear 7 side is partly cut out and the tooth portion 4a on the carrier 5 side is all cut off, but this may be reversed. In other words, the configuration may be such that all of the teeth 6a on the ring gear 7 side are omitted and the teeth 4a on the carrier 5 side are partially cut off.

  However, in the example planetary reduction mechanism 3, a certain number or more of tooth portions 6 are necessary on the ring gear 7 side in order to smoothly mesh with the plurality of planet gears 8. On the other hand, the carrier 5 only needs to have the teeth 4 that only stop the rotation of the carrier 5. Therefore, it is preferable to provide the tooth portion 6a on the ring gear 7 side so as to be partially cut away. Thereby, the planet gear 8 can be smoothly meshed with the tooth portion 6b of the ring gear 7 where the notch 10 is not provided and the tooth portion 6b without the notch 10 (see FIG. 6).

  Next, another example of the rotational power device in the embodiment of the present invention will be described with reference to FIGS. The basic configuration of other examples is the same as the configuration of the above example. Therefore, the same components as those in the example are denoted by the same reference numerals, detailed description thereof is omitted, and only characteristic configurations different from the example are described in detail below.

  In another example, both the notch shape provided in the tooth portion 4a on the carrier 5 side which is the drive gear A and the notch shape provided on the tooth portion 6a on the ring gear 7 side which is the meshing gear B, A notch 10 is formed on one end side in the sliding direction s of each tooth portion 4a, 6a. The notch 10 of the tooth portion 6a of the ring gear 7 is formed on one end side in the sliding direction s on the meshing start region P side of the tooth portion 6a, as in the example.

  The notch 10 of the tooth portion 4a of the carrier 5 is formed on one end side in the sliding direction s on the meshing start region P side of the tooth portion 4a, as in the case of the ring gear 7 (see FIG. 10). Further, in the tooth portion 4b not provided with the notch 10 on the carrier 5 side, a tapered surface 12 similar to that on the ring gear 7 side is formed at the corner portion of the sliding direction s end in the meshing start region P. Yes.

  In another example of the rotational power device having the above-described configuration, for example, the ring gear 7 that was originally in a position where it does not mesh is slid to the carrier 5 side. Then, first, in the meshing start region P, the tooth portion 6b arranged in the circumferential direction in the ring gear 7 and the tooth portion 4b arranged in the circumferential direction in the carrier 5 are separated. It will mesh smoothly. So far, this is the same as the example.

  When the teeth 4b and 6b are engaged in the engagement start region P, the rotation of the carrier 5 is prohibited, and the carrier 5 is further slid in the sliding direction s while maintaining the positional relationship in the rotation direction r. And if it slides to the position beyond the mutual mesh | engagement start area | region P, in addition to tooth parts 4b and 6b which are not providing the notch 10 of the carrier 5 and the ring gear 7, tooth parts 4a and 6a At the portion where the notch 10 is not provided, the meshing is started. That is, when the ring gear 7 is slid to the back, all the tooth portions 4 and 6 of the carrier 5 and the ring gear 7 are fitted with no gap therebetween, thereby realizing a reliable engagement in a large area. Is done.

  Next, another example of the rotary power device according to the embodiment of the present invention will be described with reference to FIGS. In addition, among the configurations of other examples, the same reference numerals are given to the same configurations as those already described in one example or other examples, and detailed description will be omitted, and only the characteristic configurations of other examples will be described below. Detailed description.

  Furthermore, in the rotating power device of another example, the irregular ratio can be changed by switching the meshing between the spur gears 20 and 21 arranged in the gear box 14. In the gear box 14, a sun gear 9 that is rotationally driven by the motor 1, a plurality of planet gears 8 that mesh with the sun gear 9, a carrier 5 that rotatably supports each planet gear 8, and each planet gear 8 mesh. A one-stage planetary speed reduction mechanism 3 including a matching ring gear 7 is formed. A plurality of types (two types in the illustrated example) of spur gears 20 having different diameters are integrally connected to the carrier 5. In the following, the large diameter spur gear 20 is denoted by reference numeral 20a, and the small diameter spur gear 20 is denoted by reference numeral 20b.

  A small-diameter spur gear 21 a that meshes with the large-diameter spur gear 20 a and a large-diameter spur gear 21 b that meshes with the small-diameter spur gear 20 b are fixed to the box output shaft 22 in the gear box 14. In this state, it is slidably arranged. As shown in FIG. 12A, when the box output shaft 22 is positioned on the right side in the figure, the spur gear 20b and the spur gear 21b are engaged, and the spur gear 20a and the spur gear 21a are disengaged. Further, as shown in FIG. 12C, when the box output shaft 22 is positioned on the left side in the figure, the spur gear 20a and the spur gear 21a are engaged, and the spur gear 20b and the spur gear 21b are disengaged. The

  The box output shaft 22 is slid through a lever 23 protruding outward through the opening of the gear box 14, and the spur gear 20a and the spur gear 21a are engaged to transmit rotational power to the box output shaft 22. The state in which the spur gear 20b and the spur gear 21b are engaged and the rotational power is transmitted to the box output shaft 22 is selectively switched. That is, the reduction ratio can be switched by operating the lever 23.

  In still another example of the rotary power device, the spur gear 20 (large diameter and small diameter spur gears 20a, 20b) is the drive gear A, and the spur gear 21 (small diameter and large diameter spur gear 21a) meshing with the drive gear A. , 21b) is the meshing gear B.

  In the spur gears 20a and 20b, which are the drive gear A, a large number of tooth portions 4 including tooth portions 4a and 4b similar to those of the carrier 5 of one example or another example are arranged on the outer peripheral surface. Further, in the spur gears 21a and 21b which are the meshing gears B, a large number of tooth portions 6 including tooth portions 6a and 6b similar to those of the carrier 5 of other examples are arranged on the outer peripheral surface. That is, the notch 10 is formed in the tooth portion 4a on the spur gear 20a, 20b side and the tooth portion 6a on the spur gear 21a, 21b side on one end side in the sliding direction s on the meshing start region P side. .

  In another example of the rotational power device having the above-described configuration, for example, the spur gear 21a that was originally in a position not meshed is slid to the corresponding spur gear 20a side (see FIG. 15A). Then, first, in the meshing start region P, one or more teeth 6b are arranged in the circumferential direction in the spur gear 21a, and one or more teeth are arranged in the circumferential direction in the spur gear 20a. The portion 4b meshes smoothly (see FIG. 15B).

  When the teeth 4b and 6b are engaged with each other in the meshing start region P, rotational power is transmitted from the spur gear 20a to the spur gear 21b, and the spur gear 21b further slides in the sliding direction s while rotating integrally. It is slid to. And when it slides to the position beyond the meshing start area P of each other, the notch 10 is provided in addition to the tooth portions 4b, 6b not provided with the notch 10 of the spur gear 20a and the spur gear 21a. The tooth portions 4a and 6a that have been started to engage with each other. That is, at the stage where the spur gear 21a is slid to the back, all the tooth portions 4 and 6 of the spur gear 20a and the spur gear 21b are fitted with no gap therebetween, thereby realizing a reliable engagement in a large area. (See FIG. 15C).

  The meshing between the spur gear 20a and the spur gear 21a has been described above, but the same applies to the meshing between the spur gear 20b and the spur gear 21b. The meshing between the spur gear 20b and the spur gear 21b is performed in such a manner that the meshing between the spur gear 20a and the spur gear 21a shown in FIG.

It is a perspective view which shows the carrier and ring gear of an example rotary power apparatus in embodiment of this invention. It is a partial enlarged view of a ring gear same as the above. It is a schematic sectional drawing which shows a mode that a carrier and ring gear same as the above mesh. FIG. 4 is a schematic cross-sectional development view taken along the line XX of FIG. 3, and (a) to (c) sequentially show the state of meshing. It is sectional drawing corresponding to FIG. 4 which shows the modification of a ring gear. It is sectional drawing of the gear box which accommodated the carrier and ring gear same as the above, (a)-(c) has shown in order that the reduction ratio is switched. It is a disassembled perspective view which shows the mechanism in a gearbox same as the above. It is a whole sectional view of the rotary power equipment same as the above. It is a perspective view which shows the carrier and ring gear of the rotary power apparatus of the other example in embodiment of this invention. FIG. 10 is a partially enlarged view of the ring gear of the same, and shows a case viewed from the opposite side to FIG. 9. It is a schematic sectional drawing which shows a mode that a carrier and ring gear same as the above mesh. It is sectional drawing of the gear box incorporated in the rotary power apparatus of the further another example in embodiment of this invention, (a)-(c) has shown the mode that a reduction ratio is switched in order. It is a disassembled perspective view which shows the mechanism in a gearbox same as the above. It is a schematic side view explaining meshing of spur gears that constitute the same mechanism. It is a schematic sectional drawing of the YY line | wire of FIG. 14, (a)-(c) has shown the mode that it meshes | engages in order. It is a perspective view which shows the carrier and ring gear of the conventional rotary power apparatus.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Motor 3 Planetary reduction mechanism 4, 4a, 4b Tooth part 5 Carrier 6, 6a, 6b Tooth part 7 Ring gear 8 Planet gear 12 Tapered surface 20 Spur gear 21 Spur gear A Drive gear B Engagement gear P Engagement start area s Slide direction

Claims (5)

A drive gear having a large number of teeth in the circumferential direction, a meshing gear having a large number of teeth in the circumferential direction, and a motor for rotating the drive gear, and meshing along the rotation axis direction of the drive gear A rotating power device that can be switched between a position where the teeth of the drive gear and the meshing gear mesh with each other and a position where the meshing gear does not mesh with each other. In the region, a part of the tooth portions of the drive gear and a large number of tooth portions of the meshing gear so that only one or a plurality of tooth portions positioned in the circumferential direction are meshed with each other. Some of the teeth are provided in a notch shape, and in the teeth not provided with a notch shape, a convex curved taper surface is provided at the corner of the sliding direction end in the meshing start region. Formed and provided in the notch shape of the meshing gear In part, the rotational power device, characterized in that the formation of the concave curved surface of the tapered surface connecting the end face of the end face and the meshing gear cutout portion. Upper Symbol cutout shape of meshes fit gear has a shape formed by cutting a sliding direction end side of the tooth part, the notch shape of the driving gearing is a shape obtained by cutting the teeth over the entire sliding direction The rotary power device according to claim 1.   2. The rotary power device according to claim 1, wherein both of the cutout shapes of the drive gear and the meshing gear are cut out at one end side in the sliding direction of the tooth portion. The drive gear is a carrier, the meshing gear is a slidable ring gear, and a planetary gear that is rotatably supported by the carrier is provided to form a planetary gear mechanism with a variable reduction ratio. The rotative power apparatus as described in any one of Claims 1-3 characterized by the above-mentioned. Drive gear and meshing gear are both spur gears, rotational power according to any one of claims 1 to 3, wherein the reduction ratio can be freely changed by switching the power transmission spur gears Equipment .

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