JP2011007296A - Epicycle reduction gear - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve a degree of freedom in design of a main bearing vicinity of a carrier, and to shorten a size in a radial direction of an epicycle reduction gear without reducing strength of the main bearing vicinity.SOLUTION: The epicycle reduction gear 40 extracting a relative rotating component of external gears 51-53 and an internal gear 56 as output includes: a pair of first and second carriers 62, 64 disposed in axial both sides of the external gears 51-53; and an inner pin (a column part) 60 piercing the external gears 51-53 to connect the first and second carriers 62, 64. The inner pin 60 has a fit-in end 60E fitting in and fixing the second carrier 64, and a body 60B piercing the external gears 51-53. In the inner pin 60, an axis circle diameter ER1 of an axis Oe of the fit-in end 60E is smaller than an axis circle diameter BR2 of an axis Ob of the body 60B.

Description

  The present invention relates to a planetary gear reduction device.

  For example, Patent Document 1 discloses a planetary gear reduction device as shown in FIG.

  The planetary gear reduction device 10 includes three external gears 11 to 13 and an internal gear 14 with which the external gears 11 to 13 are internally meshed, and the external gears 11 to 13 and the internal gear 14. The relative rotation component is taken out as an output.

  When the input shaft 16 is rotated by a motor (not shown), the eccentric bodies 17 to 19 integrally formed on the outer periphery of the input shaft 16 are rotated. Since the outer circumferences of the eccentric bodies 17 to 19 are eccentric with respect to the axis of the input shaft 16, the external gears 11 to 13 incorporated in the outer circumferences of the eccentric bodies 17 to 19 are respectively rotated when the input shaft 16 rotates once. Swing once. As a result, the meshing positions of the internal gear 14 and the external gears 11 to 13 are sequentially shifted in the circumferential direction, and the external gears 11 to 13 correspond to the difference in the number of teeth of the two gears with respect to the internal gear 14. Rotate relatively as much as you can.

  On the other hand, inner pin holes 11A to 13A are respectively formed through the external gears 11 to 13, and the inner roller 20 and the inner pin 22 are loosely fitted into the inner pin holes 11A to 13A. First and second carriers 24 and 26 are arranged on both sides in the axial direction of the external gears 11 to 13, and are connected by a connecting bolt 28 via an inner pin 22. The first and second carriers 24 and 26 are supported on the casing 34 by first and second main bearings 30 and 32.

  The relative rotation of each of the external gears 11 to 13 with respect to the internal gear 14 is caused by the first and second carriers 24 and 26 via the inner pin 22 and the inner roller 20 passing through the external gears 11 to 13. It is taken out. As a result, a reduction with a large reduction ratio corresponding to (the number of teeth difference between the internal gear 14 and the external gears 11 to 13) / (the number of teeth of the external gears 11 to 13) can be realized in one stage. . The swing component of the external gears 11 to 13 is absorbed by loose fitting (fitting with a gap) between the inner pin holes 11A to 13A and the inner pin 22 (inner roller 20).

JP 2006-292065 A

  In this type of structure, the root 22A of the inner pin 22 is the most difficult in terms of strength. In order to increase the strength of the root 22A of the inner pin 22, it is effective to increase the diameter 22d1 of the inner pin 22 or increase the axial center diameter 22R1 of the axial center O1 of the inner pin 22. However, in the conventional structure, when trying to increase the diameter 22d1 of the inner pin 22 and the shaft center circular diameter 22R1, in particular, the inner ring raceway surface 32A of the second main bearing 32 of the second carrier 26 and the inner pin of the second carrier 26 are increased. There arises a problem that it is difficult to secure the dimension L2 between the recess 26A. Since the dimension L2 corresponds to the “radial thickness” of the portion supporting the inner ring raceway surface 32A of the second main bearing 32, it is necessary to ensure a sufficient size. However, if the diameter 22d1 of the inner pin 22 and the axial center circle diameter 22R1 are increased, the dimension L2 inevitably tends to decrease.

  For this reason, if the strength of the root 22A of the inner pin 22 is secured to be high while securing a sufficient size with respect to the dimension L2, as a result, the radial direction dimension of the entire reduction gear must be increased. There were many.

  The present invention has been made in order to solve such a conventional problem, and while maintaining the strength in the vicinity of the main bearing without increasing the radial dimension of the entire reduction gear, The problem is to further improve the strength of the column portion (inner pin) connecting the carriers.

  The present invention relates to a planetary gear reduction device that includes an external gear and an internal gear that is internally meshed with the external gear, and that takes out a relative rotational component between the external gear and the internal gear as an output. A pair of carriers disposed on both sides in the axial direction of the toothed gear, and a column part that connects the pair of carriers through the external gear, and the column part is fitted and fixed to the carrier. An insertion end portion, and a main body portion penetrating the external gear, and the axial center diameter of the shaft center of the insertion end portion is larger than the axial center diameter of the shaft center of the main body portion. The above-mentioned problem is solved by adopting a configuration in which is smaller.

  Here, the axial center diameter of the axis of the main body means the radius of a circle passing through the axis of the main body centering on the axis of the planetary gear speed reducer, and the axial center of the axis of the fitting end The diameter means the radius of a circle passing through the shaft center of the fitting end portion centering on the shaft center of the planetary gear reduction device.

  According to the present invention, it has been difficult to achieve both of the above, ensuring the strength of the column connecting the pair of carriers and ensuring the strength near the main bearing (particularly the dimension between the inner ring raceway surface and the inner pin recess of the carrier). (Ensuring the dimension L2 in the conventional example) can be satisfactorily achieved without increasing the radial dimension of the entire speed reducer.

  That is, in the present invention, the above-described problem (design dilemma) has been solved by paying attention to the space “inside the reduction gear in the radial direction” of the inner pin recess. Specifically, the main body portion and the fitting end portion of the inner pin that have been conventionally designed as an integral member having the same axis are regarded as separate members and are designed separately including the axis. Inspired. That is, in the present invention, the diameter of the center axis of the shaft center of the fitting end (to the carrier) is larger than the diameter of the center axis of the main body (through the external gear) of the column. To be small. As will be described in detail later, according to this configuration, it is possible to design various variations (increasing the degree of freedom in design), and in particular, it becomes easy to ensure the strength near the main bearing, and as a result, there is no hindrance. The strength of the base portion of the column portion that becomes the neck can be further increased.

  According to the present invention, the strength of the column connecting the pair of carriers can be further improved while maintaining the strength in the vicinity of the main bearing without increasing the overall radial size of the reduction gear.

Sectional drawing of the planetary gear speed reducer which concerns on an example of embodiment of this invention. Sectional view along the line II-II in FIG. (A) Front view and (B) Side view of the first carrier employed in the above embodiment (with the inner pins as the pillars integrated) Partial enlarged front view showing a modification of the insertion end of the inner pin (column) Sectional drawing of the planetary gear speed reducer which concerns on an example of other embodiment of this invention. Sectional view along line VI-VI in FIG. (A) Front view and (B) Side view of the first carrier extracted and shown employed in the other embodiment (integrated with the carrier pin as the pillar). Partial sectional view showing an example of a conventional planetary gear reduction device

  Hereinafter, an example of an embodiment of the present invention will be described in detail based on the drawings.

  FIG. 1 is a cross-sectional view showing a planetary gear reduction device according to an example of an embodiment of the present invention, and FIG. 2 is a cross-sectional view taken along the line II-II in FIG.

  This planetary gear reduction device 40 includes an input shaft 42, three eccentric bodies 44 to 46, three external gears 51 to 53, and an internal gear 56, and swings the external gears 51 to 53. The relative rotation components of the external gears 51 to 53 and the internal gear 56 are extracted as output. This configuration is basically the same as the conventional example described above.

  However, in this embodiment, as shown in FIG. 2, the internal teeth of the internal gear 56 are constituted by cylindrical outer pins 56 </ b> B incorporated in every other arc-shaped groove 56 </ b> A. Even in such a configuration, the transmission capacity is slightly reduced as compared with the case where the outer pins 56B are arranged in all the grooves 56A, but the mechanical relative movement between the external gears 51 to 53 and the internal gear 56 ( The same principle can be obtained as the principle of deceleration). The number of mechanistic internal teeth is the number of the grooves 56A. The number of grooves 56A (60 in this example) is one more than the number of external teeth (59 in this example) of each external gear 51-53.

  Returning to FIG. 1, first and second carriers 62 and 64 are arranged on both sides of the external gears 51 to 53 in the axial direction. Inner pin holes 51A to 53A are formed through the external gears 51 to 53, and the inner roller 58 and the inner pin (column part) 60 are loosely fitted in the inner pin holes 51A to 53A. The first and second carriers 62 and 64 are connected by the inner pin 60. Specifically, one end of the inner pin 60 is integrated with the first carrier 62. The other end of the inner pin 60 includes a fitting end portion 60 </ b> E that is fitted into the inner pin recess 64 </ b> A of the second carrier 64.

  That is, the inner pin 60 protrudes from the first carrier 62 in the axial direction, and has a fitting end portion 60E fitted and fixed to the second carrier 64, and a main body portion that passes through the external gears 51 to 53. 60B. The inner pin 60 is connected to the second carrier 64 via the connecting bolt 72 after the insertion end 60E is inserted into the inner pin recess 64A (press-fitting in the present embodiment). A more specific configuration of the inner pin (column part) 60 will be described in detail later.

  The first and second carriers 62 and 64 are thus connected by the inner pin 60 and rotate to the casing 70 (integrated with the internal gear 56) via the first and second main bearings 66 and 68, respectively. It is supported freely. The first and second main bearings 66 and 68 do not have an inner ring. That is, the outer peripheral surfaces 62B and 64B of the first and second carriers 62 and 64 also serve as inner ring raceway surfaces of the first and second main bearings 66 and 68.

  Here, the configuration of the inner pin (column part) 60 will be described in detail with reference to FIG. 3A and 3B show the first carrier 62 employed in the present embodiment (in which the inner pin 60 as the pillar portion is integrated), where FIG. 3A is a front view and FIG. 3B is a side view. It is.

  The axial center diameter ER of the insertion end portion 60E of the insertion end portion 60E of the inner pin 60 is formed smaller than the axial center diameter BR of the shaft center Ob of the main body portion 60B by a deviation amount δR. (BR-ER = δR). Here, “the axial center diameter ER of the axial center Oe of the insertion end portion 60E” is an insertion centered on the axial center of the planetary gear speed reducer 40 (in this example, coincident with the axial center Og of the input shaft 42). It means the radius of a circle passing through the axis Oe of the end portion 60E. Further, “the axial center diameter BR of the axis Ob of the main body 60B” means the radius of a circle passing through the axis Ob of the main body 60B with the axis Og of the planetary gear reduction device 40 as the center. Further, the radius Er of the insertion end portion 60E is formed to be smaller than the radius Br of the main body portion 60B by a radius difference δr (Br−Er = δr).

  The connecting bolt 72 is screwed onto the shaft center Oe of the fitting end 60E (not the shaft center Ob of the main body 60B), and connects and fixes the second carrier 64 and the fitting end 60E.

  Next, the operation of the planetary gear reduction device 40 will be described.

  When the input shaft 42 is rotated by a motor (not shown), the eccentric bodies 44 to 46 integrally formed on the outer periphery of the input shaft 42 are rotated. Since the outer circumferences of the eccentric bodies 44 to 46 are eccentric with respect to the axis Og of the input shaft 42, the external gears 51 to 53 incorporated in the outer circumferences of the eccentric bodies 44 to 46 when the input shaft 42 rotates once. Each swing once. As a result, the meshing positions of the internal gear 56 and the external gears 51 to 53 are sequentially shifted in the circumferential direction, and the external gears 51 to 53 correspond to the difference in the number of teeth of the two gears with respect to the internal gear 56. Rotate relatively as much as you can.

  The relative rotation of the external gears 51 to 53 with respect to the internal gear 56 is taken out from the first and second carriers 62 and 64 via the internal pin 60 and the internal roller 58 passing through the external gears 51 to 53. It is. As a result, a reduction with a large reduction ratio corresponding to (the number of teeth difference between the internal gear 56 and the external gears 51 to 53) / (the number of teeth of the external gears 51 to 53) can be realized in one stage. In this embodiment, since the number of teeth of the internal gear 56 corresponds to the number of the grooves 56A as described above, it is “60” (see FIG. 2). Since the number of external teeth is “59”, the reduction ratio of the planetary gear reduction device 40 is (60−59) / 59 = 1/59 after all. The swing component of the external gears 51 to 53 is absorbed by loose fitting (fitting with a gap) between the inner pin holes 51A to 53A and the inner pin 60 (inner roller 58).

  Next, a description will be given focusing on the action based on the configuration of the inner pin (column part) 60.

  As shown in FIG. 3, in this embodiment, the axial center diameter ER of the insertion end portion 60E axial center Oe of the inner pin 60 is shifted from the axial center diameter BR of the axial center Ob of the main body portion 60B by an amount δR. Only small is formed. Further, the radius Er of the fitting end portion 60E is formed to be smaller than the radius Br of the main body portion 60B by a radius difference δr. For this reason, in addition to the radial difference δr, a larger displacement δR of the axial center can be secured on the radially outer side of the insertion end portion 60E of the second carrier 64. As a result, the outer step size ΔP = ( As much as (δr + δR), more space can be secured on the radially outer side of the planetary gear device at the insertion end portion 60E.

  Therefore, it is possible to increase the axial center diameter BR of the main body portion 60B of the inner pin 60 and the radius Br of the main body portion 60B while avoiding the occurrence of strength problems near the second main bearing 68. Become. That is, the strength of the inner pin 60 can be further increased without increasing the radial dimension of the planetary gear reduction device 40 and while maintaining the strength near the second main bearing 68.

  In this example, since δr> δR, the inner step size ΔQ = (δr−δR) with respect to the inner side of the main body 60B on the radially inner side of the insertion end portion 60E of the second carrier 64 with respect to the inner side of the main body 60B. Therefore, there will be more radial space. The inner step dimension ΔQ can be a positive value, a negative value, or “zero” depending on the setting of the radius difference δr and the deviation amount δR. A setting example of the outer step dimension ΔP and the inner step dimension ΔQ will be described in detail later with reference to FIG.

  Further, in this embodiment, since the outer peripheral surface 64B of the second carrier 64 also serves as the inner ring raceway surface of the second main bearing 68, the outer peripheral surface (inner ring raceway surface) 64B (from the outer periphery of the fitting end portion 60E). The dimension L2 can be ensured more efficiently.

  Further, since the connecting bolt 72 is screwed into the shaft center Oe of the fitting end 60E (not the shaft center Ob of the main body 60B), the connecting bolt 72 exists in the center of the fitting end 60E. For this reason, the connection strength between the inner pin 60 and the second carrier 64 is ensured satisfactorily in any radial direction of the fitting end 60E.

  FIG. 4 collectively shows setting examples of the outer step dimension ΔP and the inner step dimension ΔQ.

  FIG. 4A corresponds to a setting example of the above embodiment. As already described, in this setting example, the radius Er1 of the fitting end 60E1 is smaller than the radius Br1 of the main body 60B1 (Br1> Er1). Further, the shift amount δR1 between the axial centers Ob1 and Oe1 is smaller than the radius difference δr1 between the radius Br1 of the main body 60B1 and the radius Er1 of the fitting end 60E (δr1> δR1). In this case, the outer step dimension ΔP1 is (δr1 + δR1), and the inner step dimension ΔQ1 is (δr1-δR1). Since δr1> δR1, the inner step dimension ΔQ1 is “positive”, and the position Ex1 of the fitting end 60E1 in the radial direction of the reduction gear is larger than the position Bx1 of the main body 60B1 in the radial direction of the reduction gear (outside) )Become.

  In this setting example, since the deviation amount δR1 is relatively small, the main body portion 60B1 receives the moment load received from the external gears 51 to 53 side in the main body portion 60B1 while making it possible to ensure a larger outer step size ΔP1 than in the past. The degree of concentration at the boundary portion 60K1 between the insertion end 60E1 and the insertion end 60E1 can be reduced. Further, in this setting example, since the fitting end 60E1 is completely contained in the end surface of the main body 60B1, the processing of the inner pin 60 is easy.

  FIG. 4B shows the case where the radius Er2 of the fitting end 60E2 is smaller than the radius Br2 of the main body 60B2 by an amount corresponding to the deviation δR2 between the axes Ob2 and Oe2, that is, the radius difference δr2 The case where the deviation amounts δR2 are equal (when δr2 = δR2) is shown. At this time, the outer step size ΔP2 is (δr2 + δR2) = 2 · δr2 = 2 · δR2, and the inner step size ΔQ2 is (δr2-δR2) = 0. That is, the position of the insertion end portion 60E2 on the radially inner side Ex2 of the speed reduction device coincides with the position Bx2 on the inner side of the main body portion 60B in the radial direction of the reduction device.

  In this setting example, the position Ex2 of the insertion end portion 60E2 on the radially inner side of the speed reduction device coincides with the position Bx2 of the main body portion 60B2 on the radial direction of the speed reduction device, and there is no step, so stress concentration in this portion can be avoided. . In this setting example, the inner pin 60 can be easily processed because the fitting end 60E2 is accommodated in the end surface of the main body 60B2.

  FIG. 4C shows a case where the radius Br3 of the main body 60B3 is equal to the radius Er3 of the fitting end 60E3, and the radius difference δr3 between the Br3 and Er3 is “zero”. In this case, the outer step dimension ΔP3 is equal to the axial center shift amount δR3, and the inner step dimension ΔQ3 is −δR3. That is, the position of the fitting end 60E3 is shifted inward in the radial direction of the reduction gear by the amount of deviation δR3 between the axial centers Ob3 and Oe3 with respect to the main body 60B3. In this setting example, it is possible to ensure the outside step size ΔP3 larger than the conventional one by the amount corresponding to the deviation amount δR3 between the axial centers Ob3 and Oe3.

  FIG. 4D shows an example in which the radius Er4 of the fitting end 60E4 is larger than the radius Br4 of the main body 60B4 (the radius difference δr4 is “negative”). Even if the radius Er4 of the fitting end 60E4 is larger than the radius Br4 of the main body 60B4, if the deviation amount δR4 between the axis Ob and Oe is larger than the radius difference δr4, the outer step size ΔP4 is (δR4-δr4). As a result, it is possible to secure a larger space outside the speed reducing device in the radial direction of the insertion end portion 60E4 than in the conventional case. In this setting example, the inner step difference ΔQ4 is shifted inward in the radial direction of the reduction gear by the total amount (δR4 + δr4) of the deviation amount δR4 and the radius difference δr4, but this portion is not particularly problematic when there is a margin. This setting example is excellent in that a larger space can be secured on the outside of the insertion end portion 60E4 in the radial direction of the speed reducing device while the strength at the insertion end portion 60E4 is rather increased.

  As described above, in the present invention, various selections can be made regarding the setting of the main body portion and the fitting end portion, and in either case, sufficient strength in the vicinity of the second main bearing can be secured. Therefore, as a result, the strength of the inner pin can be increased more “without trouble”.

  As can be seen from the example of FIG. 4C, in the present invention, the radius difference (δr) between the main body portion and the fitting end portion is not necessarily set (may be zero). As in the example of FIG. 4D, in some cases, the radius Er of the insertion end portion is larger than the radius Br of the main body portion 60B so long as it does not exceed the magnitude of the axial deviation (δR). It may be set large.

  Moreover, in the said embodiment, although the example in which the eccentric body was formed in the outer periphery of the input shaft arrange | positioned in the center of the planetary gear speed reducer was shown, this invention is called what is called a distribution type, for example. The present invention can be similarly applied to the column portion of the speed reduction mechanism having such a structure.

  5 to 7 show examples in which the present invention is applied to the column portion of the speed reduction mechanism having this structure.

  A transmission pinion 108 is formed on the input shaft 106 of the reduction gear 104. The transmission pinion 108 is meshed simultaneously with three distribution gears 130A to 130C (only 130A is shown). Each distribution gear 130A-130C is integrated with three eccentric body shafts 144A-144C.

  The eccentric body shaft 144A includes eccentric bodies 160A and 162A that are eccentric from the axis of the eccentric body shaft 144A. Similarly, the eccentric body shafts 144B and 144C include the eccentric bodies 160B and 162B and the eccentric bodies 160C and 162C (the eccentric bodies 160B, 162B, 160C, and 162C are not shown).

  The eccentric bodies at the same position in the axial direction of the eccentric body shafts 144A to 144C, for example, the eccentric body 160A of the eccentric body shaft 144A, the eccentric body 160B of the eccentric body shaft 144B, and the eccentric body 160C of the eccentric body shaft 144C are identical to each other. Built in with an eccentric phase of. The eccentric body 162A of the eccentric body shaft 144A, the eccentric body 162B of the eccentric body shaft 144B, and the eccentric body 162C of the eccentric body shaft 144C are also incorporated with the same eccentric phase. External gears 166 are fitted to the eccentric bodies 160A to 160C. An external gear 168 is fitted to the eccentric bodies 162A to 162C.

  With these configurations, each of the eccentric body shafts 144A to 144C can rotate integrally with the respective sorting gears 130A to 130C in the same direction at the same speed, and the eccentric body shafts 144A to 144C can be rotated by the rotation of the eccentric body shafts 144A to 144C. 160A, 160B, and 160C rotate in the same phase as a set, and similarly, the set of eccentric bodies 162A, 162B, and 162C rotate in the same phase. The eccentric phase of the set of eccentric bodies 160A, 160B, 160C and the eccentric phase of the set of eccentric bodies 162A, 162B, 162C are shifted from each other by 180 degrees, and the eccentric phase difference of the external gears 166, 168 is 180 °. It is.

  The two external gears 166 and 168 are in mesh with the internal gear 172. The internal gear 172 is integrated with the casing 120. The internal teeth of the internal gear 172 are constituted by external pins 174. Here, every two outer pins 174 are omitted in consideration of weight reduction and cost reduction. Even in this configuration, the same mechanical relative motion (deceleration principle) between the external gears 166 and 168 and the internal gear 172 can be obtained.

  Here, first and second carriers 146 and 148 are disposed on both axial sides of the external gears 166 and 168, and are rotatably supported by the casing 120 via the first and second main bearings 178 and 180, respectively. ing. The second carrier 148 is fixed and connected to the carrier pins (column portions) 184A to 184C by a connecting bolt (only the bolt hole 182 is shown). In this embodiment, carrier pins (column portions) 184A to 184C pass through carrier pin holes 166A to 166C and 168A to 168C (not shown) of the external gears 166 and 168, and the carrier pins 184A to 184C pass through the carrier pins 184A to 184C. On the other hand, the same configuration as in the previous embodiment can be applied (for the portion indicated by arrow P in FIG. 5).

  That is, when attention is paid to the carrier pin 184A for convenience, the carrier pin 184A has a fitting end 184E5 fitted and fixed to the second carrier 148, and a main body 184B5 penetrating the external gears 166 and 168. . Then, the axial center diameter ER5 of the shaft center Oe5 of the insertion end 184E5 is formed smaller than the axial center diameter BR5 of the shaft center Ob5 of the main body 184B5 by the deviation amount δR5. The same configuration is adopted for the other carrier pins (column portions) 184B and 184C.

  Even with this configuration, it is possible to secure a large outer step size ΔP5 at the radially outer position of the planetary gear reduction device 104 of the carrier pins 184A to 184C, and the implementation of FIGS. 1 to 3 (FIG. 4A) described above. The effect substantially equivalent to the form can be obtained as it is.

  In the above embodiment, an example is shown in which one end of the column portion (inner pin or carrier pin) is integrally formed with one of the pair of first and second carriers (first carrier). However, the present invention can also be applied to a structure in which the pillar portion is connected to both of the pair of carriers via a connecting bolt. In the case of this configuration, the present invention can be applied to the fitting end portions of both carriers.

  In the above embodiment, the connecting bolt is screwed onto the shaft center of the insertion end portion. However, in the present invention, the connection bolt for connecting the column portion and the carrier is not necessarily on the shaft center of the insertion end portion. There is no need to screw it in, and it may be displaced to the outside in the radial direction or inside as appropriate depending on the arrangement relationship with other members.

  Furthermore, in the above embodiment, the inner rings of the bearings (first and second main bearings) in which the first and second carriers support the first and second carriers so as to be rotatable relative to the casing of the planetary gear reduction device. However, the bearing may have a dedicated inner ring.

  In addition, the insertion of the insertion end portion into the carrier does not necessarily need to be bolted after being press-fitted as in the above-described embodiment, and priority is given to ease of assembly. For example, only press-fitting (no bolt) is used. Alternatively, a structure may be used in which a gap is fitted and then fixed with a bolt.

DESCRIPTION OF SYMBOLS 40 ... Planetary gear reduction device 42 ... Input shaft 44-46 ... Eccentric body 51-53 ... External gear 56 ... Internal gear 60 ... Internal pin (column part)
60B ... Body part 60E ... Fitting end part 62, 64 ... First and second carriers 64A ... Inner pin recess ER ... Axial center diameter of insertion end part BR ... Axis center diameter of main part δR ... Amount of deviation of axis

Claims (4)

In a planetary gear reduction device comprising an external gear and an internal gear with which the external gear internally meshes, and taking out a relative rotational component between the external gear and the internal gear as an output,
A pair of carriers disposed on both sides in the axial direction of the external gear; and a pillar portion that connects the pair of carriers through the external gear,
The column portion has a fitting end portion that is fitted and fixed to the carrier, and a main body portion that penetrates the external gear, and
A planetary gear speed reduction device characterized in that the diameter of the center axis of the shaft center of the fitting end is smaller than the diameter of the center axis of the axis of the main body. In claim 1,
One end of the column portion is formed integrally with one of the pair of carriers. In claim 1 or 2,
The planetary gear reduction device, wherein the carrier and the column portion are connected and fixed by screwing a connecting bolt onto the shaft center of the fitting end portion. In any one of Claims 1-3,
The planetary gear reduction device, wherein the carrier also serves as an inner ring of a bearing that supports the carrier so as to be rotatable relative to the casing of the planetary gear reduction device.

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