JP6453135B2 - Eccentric rocking gear device - Google Patents

Description

  The present invention relates to an eccentric oscillating gear device.

  Patent Document 1 discloses an eccentric oscillating gear device. This gear device includes an external gear and an internal gear. The gear device takes out the relative rotation between the external gear and the internal gear obtained by eccentrically swinging the external gear as an output.

  For this reason, the gear device includes a crankshaft for swinging and rotating the external gear. Further, a carrier for supporting the crankshaft and a crankshaft bearing disposed between the crankshaft and the carrier are provided. The carrier has a bearing hole in which the crankshaft bearing is disposed.

  The bearing hole is a bottomed hole having a bottom. A through hole for allowing the lubricant to flow is formed in the center in the radial direction of the bottom of the bearing hole.

JP 2014-206249 A (FIG. 1)

  In the gear device disclosed in Patent Document 1, it is sometimes required to disassemble (separate) the crankshaft bearing from the carrier of the gear device for maintenance and replacement of parts. However, since the bearing hole of the crankshaft bearing has a bottom, there is a problem that it is difficult to remove the outer ring from the bearing hole of the carrier.

  The present invention has been made to solve the above-described conventional problems, and is intended to facilitate disassembly of an outer ring of a crankshaft bearing of an eccentric oscillating gear device from a bearing hole of a carrier. It is an issue.

The present invention provides an eccentric oscillating gear device comprising a crankshaft, a carrier that supports the crankshaft, and a crankshaft bearing that is disposed between the crankshaft and the carrier. A bearing hole in which the crankshaft bearing is disposed, and the bearing hole is a bottomed hole having a bottom, and the bottom of the bearing hole penetrates in the axial direction and through which the lubricant flows. The axial center of the through hole is offset from the axial center of the bearing hole, and the through hole is an axial end surface of the outer ring of the crankshaft bearing near the through hole and the rolling element. The above-mentioned problem is solved by adopting a configuration that overlaps the axial end surface on the side close to the through hole when viewed from the axial direction.

  In the present invention, the axial center of the through hole of the bearing hole of the crankshaft bearing is offset from the axial center of the bearing hole, and the through hole and the outer ring of the crankshaft bearing overlap when viewed from the axial direction. Therefore, when disassembling the crankshaft bearing from the carrier, for example, a pin member or the like is inserted from the opposite outer ring side into a through hole overlapping with the outer ring of the crankshaft bearing when viewed from the axial direction, and penetrates through the pin member. You can hit the outer ring with a hammer etc. through the hole.

  Thus, the outer ring can be easily disassembled from the bearing hole of the carrier.

  According to the present invention, the outer ring of the crankshaft bearing of the eccentric oscillating gear device can be easily disassembled from the bearing hole of the carrier.

Sectional drawing which shows the whole structure of the eccentric rocking | fluctuation type gear apparatus which concerns on an example of embodiment of this invention. Exploded view showing the main parts of the gear unit exploded The front view which shows the state in which the outer ring | wheel of the crankshaft bearing is engage | inserted in the bearing hole of the carrier in the said embodiment. Sectional drawing which follows the arrow IV-IV line of FIG. The front view equivalent to FIG. 3 of the eccentric rocking | fluctuation type gear apparatus which concerns on the example of other embodiment of this invention, Sectional view along line VI-VI in FIG. FIG. 3 is a front view corresponding to FIG. 3 of an eccentric oscillating gear device according to still another embodiment of the present invention. Sectional drawing which follows the arrow VIII-VIII line of FIG.

  Hereinafter, examples of embodiments of the present invention will be described in detail with reference to the drawings.

  FIG. 1 is a cross-sectional view showing an overall configuration of an eccentric oscillating gear device 12 according to an example of an embodiment of the present invention, and FIG. 2 is an exploded view showing main parts of the gear device 12 in an exploded manner. .

  The gear device 12 includes external gears 14 and 15 and an internal gear 16. The gear device 12 takes out the relative rotation between the external gears 14 and 15 and the internal gear 16 obtained by eccentrically swinging the external gears 14 and 15 as an output.

  Therefore, the gear device 12 includes a crankshaft 18 for swinging and rotating the external gears 14 and 15. The gear device 12 includes a carrier 20 that supports the crankshaft 18, and crankshaft bearings 24 and 31 that are disposed between the crankshaft 18 and the carrier 20.

  More specific description will be given below.

  The gear device 12 decelerates the rotation input from the motor 29 and drives the output pinion 28 by the decelerated rotation. In the present embodiment, the motor shaft 30 of the motor 29 also serves as the input shaft of the gear device 12.

  An input gear 32 of the gear device 12 is formed at the tip of the motor shaft 30. The input gear 32 meshes with a plurality of (three in this example) sorting gears 34 at the same time. When the gear device 12 is separated from the motor 29 and handled separately, it can be considered that the sorting gear 34 constitutes the input shaft of the gear device 12. Each sorting gear 34 is incorporated in an end portion of the crankshaft 18 and can drive the crankshaft 18.

  A plurality of (three in this example) crankshafts 18 are arranged. The axis C18 of the crankshaft 18 is offset (separated) from the axis C16 of the internal gear 16 by a distance R (C16-C18). Eccentric bodies 36 and 37 are integrally provided on the crankshaft 18.

  The outer periphery of the eccentric bodies 36 and 37 is eccentric with respect to the axis C18 of the crankshaft 18. In this example, two eccentric bodies 36 and 37 are provided on each crankshaft 18. The eccentric phase difference between the eccentric body 36 and the eccentric body 37 is 180 degrees. The eccentric phases of the eccentric bodies 36 at the same position in the axial direction of the crankshafts 18 and the eccentric bodies 37 are the same.

  Each crankshaft 18 passes through the two external gears 14 and 15. The external gears 14 and 15 are incorporated on the outer circumferences of the eccentric bodies 36 and 37 through eccentric body bearings 40 and 42 so as to be able to swing eccentrically. The external gears 14 and 15 are in mesh with the internal gear 16.

  In this example, the internal gear 16 has an internal gear main body 16A integrated with the casing main body 44A of the casing 44, and a cylindrical shape rotatably incorporated in a groove portion 16B formed in the internal gear main body 16A. An internal tooth pin 16C. The internal tooth pin 16 </ b> C constitutes an internal tooth of the internal gear 16. The number of internal teeth of the internal gear 16 (the number of internal teeth pins 16C) is slightly larger (only 1 in this example) than the number of external teeth of the external gears 14 and 15.

  The casing 44 of the gear device 12 includes the casing body 44A, the anti-load side cover 44B, and the load side cover 44C. The casing 43 of the motor 29 is connected to the anti-load side cover 44 </ b> B of the gear device 12 via the motor bolt 71. The anti-load side cover 44 </ b> B and the casing body 44 </ b> A are connected via an anti-load side bolt 72. Further, the casing body 44 </ b> A and the load side cover 44 </ b> C are connected via a load side bolt 73.

  The crankshaft 18 is supported by the carrier 20 via a pair of crankshaft bearings 24 and 31. The carrier 20 includes a first carrier 21 disposed on the axial load side of the external gears 14 and 15, a second carrier 22 connected to the first carrier 21 via a carrier pin 23 and a carrier bolt 74, Is provided. In this embodiment, the carrier pin 23 is formed integrally with the first carrier 21 and penetrates the external gears 14 and 15. The second carrier 22 is disposed on the axially opposite load side of the external gears 14 and 15.

  In this embodiment, the crankshaft bearings 24 and 31 are incorporated in the carrier 20 face to face. The load-side crankshaft bearing 24 is supported by the first carrier 21. The crankshaft bearing 31 on the opposite load side is supported by the second carrier 22. In the gear device 12, the present invention is applied in a configuration in which the first carrier 21 supports the load-side crankshaft bearing 24. The configuration in which the first carrier 21 supports the load-side crankshaft bearing 24 will be described in detail later.

  An output shaft portion 46 is integrated on the load side of the first carrier 21. In the output shaft portion 46, a connection portion 47, a bearing arrangement portion 48, and an outer spline portion 49 are formed in this order from the first carrier 21 side. An output shaft bearing 50 is arranged in the bearing arrangement portion 48. In this example, the output shaft bearing 50 is constituted by a self-aligning roller bearing, and the output shaft portion 46 is supported by the casing 44.

  A retaining ring 51 is fitted into the output shaft bearing 50. The retaining ring 51 is sandwiched between the casing main body 44A of the casing 44 and the load side cover 44C. Thereby, the retaining ring 51 positions the output shaft bearing 50 in the axial direction with respect to the casing main body 44A.

  An outer spline portion 49 is formed on the load side of the bearing arrangement portion 48 of the output shaft portion 46. The output pinion 28 is formed with an inner spline portion 33 that engages with the outer spline portion 49. The output pinion 28 is fixed to the output shaft portion 46 in the circumferential direction by the engagement of the outer spline portion 49 and the inner spline portion 33. The output pinion 28 is fixed to the output shaft portion 46 in the axial direction by a fixing plate 52 and a pinion bolt 75.

  1 and 2, reference numerals 56 and 57 are oil seals, reference numeral 58 is a collar, and reference numeral 59 is a roller bearing that supports the second carrier 22 on the casing 44. Reference numerals 81 and 82 denote lubricant passages for supplying the lubricant to the engaging portion between the outer spline portion 49 of the output shaft portion 46 and the inner spline portion 33 of the output pinion 28.

  In the following, referring to FIG. 1 and FIG. 2 together with FIG. 3 and FIG. 4, a configuration in which the outer ring 25 of the crankshaft bearing 24 can be disassembled from the first carrier 21 of the gear device 12 will be described in detail. . 3 is a front view of the first carrier 21, and FIG. 4 is a cross-sectional view taken along the line IV-IV in FIG. FIG. 4 shows a state where the outer ring 25 of the crankshaft bearing 24 is left in the bearing hole 54.

  Note that FIG. 4 is not necessarily a cross section taken along the line IV-IV in FIG. 3 accurately, for example, a through-hole 61 described later is indicated by a solid line in order to facilitate understanding of the features of the present embodiment. Absent. In addition to FIG. 4, for convenience of explanation, there may be a portion that does not necessarily coincide with an accurate drawing cross section.

  In the gear device 12, a crankshaft bearing 24 is disposed between the crankshaft 18 and the first carrier (carrier) 21. In this example, the crankshaft bearing 24 is constituted by a tapered roller bearing having an outer ring 25, rolling elements (conical rollers in this example) 26, and an inner ring 27.

  The first carrier 21 has a bearing hole 54 in which the crankshaft bearing 24 is disposed. Since the first carrier 21 supports the three crankshafts 18, three bearing holes 54 having the same structure are formed in the first carrier 21 at intervals of 120 degrees in the circumferential direction.

  The bearing hole axial center (axial center of the bearing hole 54) C54 coincides with the crankshaft axial center (axial center of the crankshaft 18) C18. That is, the distance R (C21-C54) from the carrier axis (axis of the first carrier 21) C21 to the bearing hole axis C54 is the distance R from the axis C16 of the internal gear 16 to the crankshaft axis C18. This is consistent with (C16-C18).

  The crankshaft bearing 24 has an outer ring 25 incorporated into the bearing hole 54 by an interference fit. The cross-sectional shape perpendicular to the shaft of the bearing hole 54 is circular, and the inner diameter of the bearing hole 54 is D54.

  The bearing hole 54 is a bottomed hole having a bottom portion 54 </ b> A in order to maintain a high support strength of the crankshaft 18. The bottom portion 54A has an outer ring positioning surface 54A1 facing the end surface 25A on the bottom side in the axial direction of the outer ring 25 of the crankshaft bearing 24 in the vicinity of the outer periphery.

  A through hole 61 penetrating in the axial direction is formed in the bottom portion 54A. In the gear device 12, the output shaft portion 46 is formed integrally with the first carrier 21. The through hole 61 is formed in a portion of the bottom portion 54A of the bearing hole 54 where the bottom portion 54A does not overlap the output shaft portion 46 when viewed in the axial direction.

  In the gear device 12, a plurality of (two in this example) through holes 61 are formed in the bottom portion 54 </ b> A of each bearing hole 54. The through-hole axis (axis of the through-hole 61) C61 is parallel to the carrier axis C21 (not necessarily parallel). The cross-sectional shape of each through hole 61 is circular, and the inner diameter is D61.

  In the gear device 12, the distances from the bearing hole axis C54 to the two through-hole axes C61 are both R (C54-C61). That is, each through-hole axis C61 is offset (separated) from the bearing hole axis C54 by a non-zero distance R (C54-C61).

  In the gear device 12, the distance from the through hole 61 to the outermost (farthest part) 61Mo with respect to the bearing hole axis C54 is R (C54-61Mo). In this embodiment, the innermost part (nearest part) 25Mi of the outer ring 25 of the crankshaft bearing 24 with respect to the bearing hole axis C54 corresponds to the innermost part of the end face 25A on the axial bottom 54A side of the outer ring 25. The distance from the bearing hole axis C54 to the innermost 25Mi is R (C54-25Mi).

  In FIG. 3, a broken line 54 (broken line indicating the bearing hole 54) coincides with the outer periphery of the outer ring 25, and a region between the broken line 54 and the innermost portion 25Mi corresponds to a region where the outer ring 25 exists. The distance R (C54-61Mo) to the outermost part 61Mo of the through hole 61 is larger than the distance R (C54-25Mi) to the innermost part 25Mi of the outer ring 25 of the crankshaft bearing 24. That is, distance R (C54-61Mo)> distance R (C54-25Mi). That is, in the gear device 12, the through hole 61 and the outer ring 25 of the crankshaft bearing 24 overlap each other when viewed from the axial direction.

  In the present embodiment, the outermost 61Mo with respect to the bearing hole axis C54 of the through hole 61 coincides with the inner periphery of the bearing hole 54 (the outer periphery of the outer ring 25). In the present embodiment, the innermost portion 61Mi of the through-hole 61 with respect to the bearing hole axis C54 is radially inward of the innermost portion 25Mi of the outer ring 25 of the crankshaft bearing 24 with respect to the bearing hole axis C54. Therefore, the entire radial length of the end surface 25A of the outer ring 25 overlaps the through hole 61 when viewed from the axial direction. In order to remove the outer ring 25, it is only necessary that 1/3 or more, preferably 1/2 or more, of the entire length in the radial direction of the end face 25A of the outer ring 25 overlaps the through hole 61 when viewed from the axial direction.

  Note that the concept of “the through hole and the outer ring of the crankshaft bearing overlap each other when viewed from the axial direction” is used here. “The through hole is the end surface on the axial bottom side of the outer ring of the crankshaft bearing (in the above example, In FIG. 25A), the outer ring overlaps with the outer ring when viewed from the axial direction. In other words, the “innermost part of the outer ring with respect to the bearing hole axial center” means “the innermost part of the outer ring with respect to the bearing hole axial center at the end surface on the bottom side in the axial direction”. More specifically, for example, when the inner diameter of the outer ring is different in the axial direction as in the present embodiment, the innermost part of the outer ring with respect to the shaft center of the bearing hole is the innermost part of the end surface on the axially bottom side of the outer ring. I mean.

  In the gear device 12, a non-zero distance R (C54-61Mi) exists from the bearing hole axis C54 to the innermost 61Mi of the through hole 61 with respect to the bearing hole axis C54. In other words, the distance R (C54-C61) from the bearing hole axis C54 to the through hole axis C61 is larger than the radius (D61 / 2) of the through hole 61. That is, in the gear device 12, the through hole 61 and the bearing hole axis C54 do not overlap each other when viewed from the axial direction.

  In the gear device 12, the distance from the carrier axis C21 to the plurality of (two) through-hole axes C61 is R (C21-C61) and is the same. That is, in the gear device 12, the plurality of through-hole axes C61 are located on the same circumference r61 with the carrier axis C21 as the center.

  In the gear device 12, in particular, the plurality of through-hole axes C61 have a straight line L connecting the carrier axis C21 and the bearing hole axis C54 in a cross section perpendicular to the carrier axis C21 (in this example, the cross section of FIG. 3). It is on a straight line L (C61-C61) orthogonal to (C21-C54) and passing through the bearing hole axis C54. In other words, the plurality of through holes 61 are formed at positions facing the bearing hole axis C54 (ends on the same diameter). That is, the plurality of through-hole axes C61 are formed at positions where the through-hole axes C61 are farthest apart from each other with the bearing hole axis C54 interposed therebetween.

  In the gear device 12, the plane P1 including a plurality (two) of through-hole axis C61 and the plane P2 including the carrier axis C21 and the bearing hole axis C54 are orthogonal to each other. Further, in the gear device 12, the plurality of through holes 61 are formed symmetrically with respect to the plane P2 including the carrier shaft center C21 and the bearing hole shaft center C54.

  In the gear device 12, the distance R (C21-C61) from the carrier axis C21 to the through-hole axis C61 is larger than the distance R (C21-C54) from the carrier axis C21 to the bearing hole axis C54. That is, distance R (C21-C61)> distance R (C21-C54). In other words, in the gear device 12, the through-hole axis C61 is located radially outside the bearing-hole axis C54.

  In the gear device 12, the distance R (C54-61Mi) from the bearing hole axis C54 to the innermost 61Mi of the through hole 61 with respect to the bearing hole axis C54 is determined from the bearing hole axis C54 to the inner ring of the crankshaft bearing 24. 27 is smaller than the distance R (C54-27Mo) from the end surface of the bottom 54A side to the outermost 27Mo with respect to the bearing hole axis C54.

  That is, in the gear device 12, the through hole 61 not only overlaps with the outer ring 25 of the crankshaft bearing 24 but also overlaps with the rolling elements 26 and the inner ring 27 of the crankshaft bearing 24 when viewed from the axial direction. That is, the through hole 61 and the outer ring 25, the through hole 61 and the rolling element 26, and the through hole 61 and the inner ring 27 overlap each other when viewed from the axial direction.

  Next, the operation of the eccentric oscillating gear device 12 will be described.

  First, the operation of the power transmission system of the gear unit 12 will be described. When the motor shaft 30 of the motor 29 rotates, the input gear 32 of the gear device 12 rotates, and the three sorting gears 34 meshed simultaneously with the input gear 32 rotate in the same direction at the same rotational speed.

  As a result, the three crankshafts 18 rotate at the same speed in the same direction, and the external gears 14 and 15 are eccentrically oscillated via the eccentric bodies 36 and 37 provided on the respective crankshafts 18. Since the number of teeth of the external gears 14 and 15 is one less than the number of teeth of the internal gear 16, the external gears 14 and 15 have one tooth with respect to the internal gear 16 every time they swing once. Relatively rotates (rotates).

  The rotation of the external gears 14 and 15 is transmitted to the crankshaft 18 passing through the external gears 14 and 15, and the carrier 20 (supporting the crankshaft 18 via the crankshaft bearings 24 and 31). The second carrier 22) connected via the first carrier 21 and the carrier pin 23 rotates. As the carrier 20 rotates, the output shaft portion 46 integrated with the first carrier 21 rotates, and the output pinion 28 connected to the output shaft portion 46 rotates.

  The gear device 12 may be disassembled for maintenance or parts replacement. Hereinafter, disassembly (assembly) of the gear device 12 will be described mainly with reference to FIG.

  In the gear device 12, the motor 29 can be pulled out in the axial direction by removing the motor bolt 71. Thereby, the motor 29 can be removed from the gear device 12 (with the input gear 32).

  By removing the anti-load side bolt 72, the anti-load side cover 44B can be removed together with the oil seal 56 and the collar 58. The removal gear 34, the roller bearing 59 of the second carrier 22, the internal tooth pin 16C of the internal gear 16 and the like can be removed by removing the non-load side cover 44B.

  Further, the second carrier 22 can be removed by removing the carrier bolt 74. By removing the second carrier 22, it is possible to remove the non-load-side crankshaft bearing 31, the external gears 14 and 15, the crankshaft 18, and the rolling element 26 and the inner ring 27 of the load-side crankshaft bearing 24.

  Through the above operation, all members incorporated on the side opposite to the load from the first carrier 21 can be disassembled except for the outer ring 25 of the crankshaft bearing 24 on the load side.

  On the other hand, the fixing plate 52 can be removed by removing the pinion bolt 75, and the output pinion 28 can be pulled out to the axial load side. As a result, the load side bolt 73 can be removed, and the load side cover 44C of the casing 44 can be disassembled.

  Then, by removing the retaining ring 51, it is possible to disassemble the casing body 44A, the output shaft bearing 50, and the first carrier 21 (with the outer ring 25 of the crankshaft bearing 24).

  Here, the outer ring 25 of the crankshaft bearing 24 is incorporated into the bearing hole 54 of the first carrier 21 with an interference fit. Therefore, conventionally, it has been difficult to take out only the outer ring 25 of the crankshaft bearing 24 from the bearing hole 54 of the first carrier 21 even if the disassembly work has been performed so far.

  However, in the present gear device 12, a through hole 61 is formed in the bottom 54A of the bearing hole 54 of the crankshaft 18, and the distance R from the through hole 61 to the outermost 61Mo with respect to the bearing hole axis C54. (C54-61Mo) is larger than the distance R (C54-25Mi) to the innermost 25Mi with respect to the bearing hole axis C54 (in the end surface 25A on the bottom side in the axial direction) of the outer ring 25 of the crankshaft bearing 24. That is, in this gear device 12, the end face 25A on the bottom side in the axial direction of the outer ring 25 of the through hole 61 and the crankshaft bearing 24 overlaps when viewed from the axial direction.

  Therefore, as shown in FIG. 4, an appropriate (for example, cylindrical) pin member 68 is inserted into the through hole 61 from the side opposite to the outer ring, and a hammer 69 is inserted through the pin member 68 through the through hole 61 of the bottom portion 54A. The end surface 25A on the bottom side in the axial direction of the outer ring 25 can be hit with the like.

  Note that the imaginary line in FIG. 4 is a view of the position of the pin member 68 (one of the through holes 61) with respect to the outer ring 25 as seen from another angle (a direction orthogonal to the plane P1). By this operation, the outer ring 25 can be disassembled (separated) from the bottom 54A of the bearing hole 54 of the first carrier 21.

  The through hole 61 is formed at a position overlapping the outer ring 25 of the crankshaft bearing 24. Therefore, the lubricant can pass through the crankshaft bearing 24 (the gap) to the output shaft portion 46 side as it is.

  For example, when the through hole is formed in the radial center of the bearing hole as in Patent Document 1, the radial direction is used to guide the lubricant that has passed through the crankshaft bearing (gap) to the output shaft side. The lubricant must be moved radially to the through hole formed in the center. Accordingly, it is necessary to provide a correspondingly large axial gap serving as a lubricant passage between the axial end face and the bottom of the crankshaft bearing. In other words, if the axial clearance between the axial end face and the bottom of the crankshaft bearing is formed large in order to improve the flowability of the lubricant, the axial length of the entire gear device increases accordingly. It becomes a trend.

  However, since the through hole 61 of the gear device 12 is formed at a position overlapping the outer ring 25 of the crankshaft bearing 24, the lubricant passes through the bottom 54A via the through hole 61 with little movement in the radial direction. it can. Therefore, the axial length of the gear unit 12 can be further shortened while maintaining a high flowability of the lubricant (however, the axial clearance between the axial end surface 18E of the crankshaft 18 and the bottom 54A is increased). It is not prohibited to take the composition).

  In the gear device 12, in addition to such basic functions and effects, the following functions and effects can be obtained.

  In the gear device 12, the distance R (C54-C61) from the bearing hole axis C54 to the through hole axis C61 is larger than the radius (D61 / 2) of the through hole 61. That is, in the gear device 12, the through hole 61 and the bearing hole axis C54 do not overlap each other when viewed from the axial direction. For this reason, the strength in the vicinity of the bearing hole 54 of the first carrier 21 can be maintained high.

  In the gear device 12, a plurality (two in this example) of through holes 61 are formed. For this reason, when the outer ring 25 is hit and separated from the bearing hole 54, the outer ring 25 can be hit at a plurality of locations in the circumferential direction. For this reason, when the outer ring 25 is struck, the outer ring 25 can be prevented from being inclined and not easily coming out of the bearing hole 54. Furthermore, since the inclination of the outer ring 25 can be reduced, the outer periphery of the outer ring 25 or the inner periphery of the bearing hole 54 can be further prevented from being damaged.

  In the gear device 12, the distances from the carrier axis C21 to the plurality of (two) through-hole axes C61 are all R (C21-C61) and are the same. That is, in the gear device 12, the plurality of through-hole axes C61 are located on the same circumference r61 with the carrier axis C21 as the center. Thereby, it can be prevented that the flow of the lubricant differs depending on the formation position of the through hole 61 when the gear device 12 rotates forward and when it rotates reversely.

  In the gear device 12, the plurality of through-hole axes C61 are orthogonal to a straight line L (C21-C54) connecting the carrier axis C21 and the bearing hole axis C54 in a cross section perpendicular to the carrier axis C21. It is located on a straight line L (C61-C61) passing through the bearing hole axis C54. In other words, in the gear device 12, the plurality of through holes 61 are formed at positions facing the bearing hole axis C54 (ends on the same diameter).

  Accordingly, it is possible to form the through hole 61 having a large inner diameter D61 while maintaining a high strength in the vicinity of the bearing hole 54 of the first carrier 21. Further, when the outer ring 25 is hit by the pin member 68, the outer ring 25 can be hit while correcting the inclination of the outer ring 25 most efficiently. That is, the plurality of through-hole shaft centers C61 are formed in positions where the through-hole shaft centers C61 are farthest apart from each other with the bearing hole shaft center C54 interposed therebetween, so that the tapping force and the labor for correcting the tilt can be minimized. Benefits are gained.

  When there are a plurality of through holes 61, the plurality of through holes may be formed symmetrically with respect to the plane P2 including the carrier axis C21 and the bearing hole axis C54. With this configuration, even when there are a plurality of (including two) through-holes, it is possible to achieve the effect of “no difference in lubricant flow is caused by forward and reverse rotation”.

  In the gear device 12, the distance R (C21-C61) from the carrier axis C21 to the through-hole axis C61 is larger than the distance R (C21-C54) from the carrier axis C21 to the bearing hole axis C54. large. In other words, in the gear device 12, the through-hole axis C61 is located radially outside the bearing-hole axis C54.

  Accordingly, it is possible to form the through hole 61 having a large inner diameter D61 while maintaining a high strength in the vicinity of the bearing hole 54 of the first carrier 21. Specifically, in the present gear device 12, by setting the distance R (C21-C61) slightly larger than the distance R (C21-C54), the above-described configuration, that is, “the plurality of through-hole axis C61 is In a cross section perpendicular to the carrier shaft center C21, on a straight line L (C61-C61) perpendicular to the straight line L (C21-C54) connecting the carrier shaft center C21 and the bearing hole shaft center C54 and passing through the bearing hole shaft center C54. The configuration of “located” is realized. As a result, the two through holes 61 can be formed at positions facing the bearing holes 54 (that is, ends on the same diameter), and the strength near the bearing holes 54 of the first carrier 21 is increased. The effect of forming the through-hole 61 having a large inner diameter D61 is enjoyed to the maximum while maintaining it.

  In the gear device 12, the through hole 61 overlaps the outer ring 25, the rolling element (conical roller) 26, and the inner ring 27 of the crankshaft bearing 24 when viewed from the axial direction. Therefore, the presence of the through-hole 61 can greatly improve the lubricity of the lubricant on the rolling surface of the rolling element 26 of the crankshaft 18 in particular.

  5 and 6 show examples of other embodiments of the present invention.

  The gear device shown in FIG. 5 has the same configuration as that of the gear device 12 of FIGS. 1 to 4 except for the configuration of the through hole 161.

  In the gear device shown in FIGS. 5 and 6, one through hole 161 is formed in each bearing hole 54. The inner diameter of the through hole 161 is D161. The inner diameter D161 is substantially equal to the radius (D54 / 2) of the bearing hole 54.

  The through-hole axis C161 (the axis C161 of the through-hole 161) is separated from the bearing hole axis C54 by approximately ½ of the inner diameter D161 of the through-hole 161. The through-hole 161 has a common tangent with the bearing hole 54, and the innermost part 161 Mi with respect to the carrier axis C <b> 21 reaches almost the center of the bearing hole 54. That is, the gear device 12 of FIGS. 5 and 6 is set to a large size in which the through hole 161 extends over the entire radial outside of the bearing hole axis C54.

  The gear device of FIGS. 5 and 6 is easy to process (low cost) because there is only one through hole 161 in each bearing hole 54.

  Other configurations are the same as those of the previous embodiment, and the same operational effects can be obtained.

  7 and 8 show examples of still other embodiments of the present invention.

  In the gear device shown in FIGS. 7 and 8, the presence of the through hole 261 is intended to favorably lubricate not only the crankshaft bearing 24 but also the output shaft bearing 50. As described above, for convenience of explanation, FIG. 8 is not an accurate cross section taken along the line VIII-VIII in FIG.

  The gear device of FIGS. 7 and 8 also has the same configuration as that of the gear device 12 of FIGS. 1 to 4 (or the gear device of FIGS. 5 and 6) except for the formation configuration of the through hole 261. That is, also in the gear device of FIGS. 7 and 8, the output shaft portion 46 having a smaller diameter than the first carrier 21 is integrated on the load side of the first carrier 21. Specifically, the outer diameter d47 of the connecting portion 47 of the output shaft portion 46, the outer diameter d48 of the bearing arrangement portion 48, and the outer diameter d49 of the outer spline portion 49 are all larger than the outer diameter d21 of the first carrier 21. Small diameter.

  An output shaft bearing 50 is disposed on the output shaft portion 46. The radius d48 / 2 of the bearing arrangement portion 48 of the output shaft bearing 50 of the output shaft portion 46 is smaller than the distance R (C21-C54) from the carrier shaft center C21 to the bearing hole shaft center C54. That is, the bearing arrangement portion 48 of the output shaft bearing 50 is located radially inward of the bearing hole axis C54.

  In the gear device shown in FIGS. 7 and 8, on the premise of this configuration, the distance R (C21-C261) from the carrier axis C21 to the through-hole axis C261 is determined from the carrier axis C21 to the bearing hole axis. The distance to C54 is set to be equal to or less than the distance R (C21-C54), that is, the same or slightly smaller (distance R (C21-C261) ≦ distance R (C21-C54)).

  Thereby, the formation position of the through hole 261 can be brought closer to the bearing arrangement portion 48 of the output shaft bearing 50 of the output shaft portion 46, and the lubricity of not only the crankshaft bearing 24 but also the output shaft bearing 50 can be improved. Can be improved.

  Configurations other than the distance R (C21-C261) from the carrier axis C21 to the through-hole axis C261 are the same as those in the previous embodiment shown in FIGS. 1 to 4, and similar effects can be obtained.

  In the above embodiment, since the output shaft portion is formed integrally with the carrier (first carrier), the through hole is seen from the bottom of the bearing hole as viewed from the output shaft portion in the axial direction. It was designed to be formed on the part that did not overlap.

  However, the output shaft portion is not necessarily formed integrally with the carrier. For example, the structure which each comprised by another member and integrated with the volt | bolt etc. may be sufficient. In this case, the through hole does not necessarily have to be formed in a portion that does not overlap with the output shaft portion when viewed from the axial direction. Since the output shaft portion can be disassembled from the carrier, even if the through hole is formed at a position overlapping the output shaft portion when viewed from the axial direction, a pin member or the like can be inserted into the through hole without any problem. This is because it can be inserted.

  Moreover, in the said embodiment, the example in which the one or two through-holes of the bottom part of a bearing hole were formed was shown. However, the number of through holes formed at the bottom of the bearing hole is not limited to this and may be three or more. Further, the cross-sectional shape of the through hole is not particularly limited to a circular shape. The through hole axis may not necessarily be parallel to the axis.

  In the above embodiment, a gear device in which the external gear is swung with respect to the internal gear by the crankshaft is shown as the eccentric rocking gear device. However, some eccentric oscillating gear devices include an eccentric oscillating gear device in which an internal gear is oscillated with respect to an external gear by a crankshaft. The present invention can be similarly applied to such an eccentric oscillating gear device in which the internal gear oscillates, and the outer ring of the crankshaft bearing can be easily disassembled from the carrier.

  Further, in the above-described embodiment, the eccentric oscillating gear device in which a plurality of crankshafts are provided at positions offset from the carrier axis is shown as the eccentric oscillating gear device. However, in an eccentric oscillating gear device, only one crankshaft is provided at the center of the carrier, and the external gear is eccentrically rocked by an eccentric body arranged at the radial center of the external gear. Some gears are moved.

  The present invention is also applicable to the case where the bearing hole of the crankshaft of such an eccentric oscillating gear device is configured with a bottomed hole. That is, even in such a gear device, by applying the present invention, the outer ring of the crankshaft bearing fitted in the bearing hole can be easily disassembled.

  Further, in the above-described embodiment, a gear device having a structure in which all the crankshafts are driven by the crankshaft gears is shown as the eccentric oscillating gear device. That is, a gear device is shown in which the crankshafts arranged in the bearing holes are all crankshafts that receive the driving force on the input shaft side.

  However, the eccentric oscillating gear device includes, for example, a plurality of crankshafts, and only a part (for example, one) of the plurality of crankshafts is driven by a driving force from the input side, There is also a gear device in which the other crankshaft is driven by a swinging motion of a swinging gear via an eccentric bearing.

  The present invention is similarly applied to such an eccentric oscillating gear device in which a crankshaft for oscillating the oscillating gear and a crankshaft driven by the oscillating motion of the oscillating gear are mixed. can do. That is, the crankshaft is not distinguished between driving and driven.

DESCRIPTION OF SYMBOLS 12 ... Gear apparatus 14, 15 ... External gear 16 ... Internal gear 18 ... Crankshaft 21 ... 1st carrier (carrier)
24 ... Crankshaft bearing 25 ... Outer ring 44 ... Casing 54 ... Bearing hole 54A ... Bottom 61 ... Through hole C21 ... Carrier shaft center C54 ... Bearing hole shaft center C61 ... Through hole shaft center

Claims (9)

In an eccentric oscillating gear device comprising a crankshaft, a carrier that supports the crankshaft, and a crankshaft bearing disposed between the crankshaft and the carrier,
The carrier has a bearing hole in which the crankshaft bearing is disposed;
The bearing hole is a bottomed hole having a bottom,
At the bottom of the bearing hole, a through hole is formed that penetrates in the axial direction and through which the lubricant flows .
The axial center of the through hole is offset from the axial center of the bearing hole,
The through hole overlaps with the axial end surface of the outer ring of the crankshaft bearing close to the through hole and the axial end surface of the rolling element close to the through hole when viewed from the axial direction. Oscillating gear device. In claim 1,
The eccentric oscillating gear device, wherein the through hole and the shaft center of the bearing hole do not overlap each other when viewed in the axial direction. In claim 1 or 2,
A plurality of the through holes are formed at the bottom of the bearing hole. In claim 3,
The eccentric oscillating gear device, wherein the shaft centers of the plurality of through holes are located on the same circumference centered on the shaft center of the carrier. In claim 3 or 4,
The shaft centers of the plurality of through holes are orthogonal to a straight line connecting the shaft center of the carrier and the shaft center of the bearing hole in a cross section perpendicular to the shaft center of the carrier, and on a straight line passing through the shaft center of the bearing hole An eccentric oscillating gear device, characterized in that: In any one of Claims 3-5,
The eccentric oscillating gear device, wherein the plurality of through holes are formed symmetrically with respect to a plane including the axis of the carrier and the axis of the bearing hole. In any one of Claims 1-6,
The eccentric oscillating gear device, wherein a distance from an axis of the carrier to an axis of the through hole is larger than a distance from an axis of the carrier to an axis of the bearing hole. In any one of Claims 1-6,
An output shaft having a smaller diameter than the carrier is integrated on the load side of the carrier,
An output shaft bearing is disposed on the output shaft portion,
The radius of the arrangement portion of the output shaft bearing of the output shaft portion is smaller than the distance from the axis of the carrier to the axis of the bearing hole, and the distance from the axis of the carrier to the axis of the through hole Is a distance from the axis of the carrier to the axis of the bearing hole or less. In any one of Claims 1-8,
The eccentric oscillating gear device, wherein the through hole and an outer ring, a rolling element and an inner ring of the crankshaft bearing overlap each other when viewed from the axial direction.

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