JP2018109428A - Eccentric oscillation type gear unit - Google Patents

Abstract

PROBLEM TO BE SOLVED: To further improve the durability of a ring arranged between a first external tooth gear and a second external tooth gear.SOLUTION: An eccentric oscillation type gear unit G comprises: an internal gear 12; a first external tooth gear 114; a second external tooth gear 214; a crank shaft 28; and a ring 20 arranged between the first external tooth gear and the second external tooth gear. The first external tooth gear includes: a tooth part 114A; a tooth part chamfer part 114B provided at least at the edge on the side of the second external tooth gear of the tooth part; and a gear side abutment surface 114C that touches the ring provided on the inside in a radial direction of the tooth part chamfer part. The ring includes a ring side abutment surface 20C that touches the gear side abutment surface. A corner part between the tooth part chamfer part of the first external tooth gear and the gear side abutment surface (a gear side outside angle portion 114P) is located along whole circumference radially outward with respect the shaft center of the internal gear than the corner part on the inner diameter side of the ring side abutment surface (a ring side inside angle portion 20Q).SELECTED DRAWING: Figure 5

Description

  The present invention relates to an eccentric oscillating gear device.

  Patent Document 1 discloses an eccentric oscillating gear device that includes an internal gear, and a first external gear and a second external gear that are internally meshed with the internal gear.

  In this gear device, the first external gear and the second external gear are internally meshed with the internal gear while being swung by the crankshaft. An insertion ring is disposed between the first external gear and the second external gear. The first external gear and the second external gear have their axial positions regulated by the insertion ring.

JP 2008-267571 A (FIG. 1)

  In such an eccentric oscillating gear device, since the first external gear and the second external gear oscillate, they are arranged between the oscillating first external gear and the second external gear. There is a problem that the durability of the insert wheel is likely to be lowered (easy to wear).

  The present invention has been made to solve such a conventional problem, and is intended to further improve the durability of the insert wheel disposed between the first external gear and the second external gear. That is the issue.

  The present invention includes an internal gear, a first external gear and a second external gear that are internally meshed with the internal gear, and a crankshaft that swings the first external gear and the second external gear. In the eccentric oscillating gear device, the first external gear includes an insertion ring disposed between the first external gear and the second external gear. A tooth portion having external teeth meshing with the internal teeth, a tooth chamfered portion provided at least on an end portion of the tooth portion on the second external gear side, and provided radially inward of the tooth chamfered portion. A gear-side abutting surface that abuts against the insertion wheel, and the insertion wheel has an abutment-side abutting surface that abuts against the gear-side abutting surface, and the teeth of the first external gear The corner between the chamfered portion and the gear-side contact surface has a diameter with respect to the shaft center of the internal gear over the entire circumference rather than the corner on the inner diameter side of the sprocket-side contact surface. With structure located toward the outside, it is obtained by solving the above problems.

  In this type of eccentric oscillating gear device, a chamfered portion may be formed at the end of the tooth portion in order to improve the processing characteristics of the end portion of the tooth portion of the first external gear. According to the inventors' life investigation, it has been confirmed that the wear of the insert ring is particularly remarkable in the gear device having such a tooth chamfered portion.

  In the present invention, the corner portion between the chamfered portion of the first external gear and the gear-side contact surface is more than the inner portion of the inner-diameter-side corner of the contact wheel-side contact surface over the entire circumference. It is comprised so that it may be located in the radial direction outer side with respect to the axial center of a toothed gear.

  Therefore, even if the first external gear is swung, it is possible to reduce the corner portion between the tooth chamfered portion and the gear-side contact surface of the first external gear from damaging the insert wheel.

  ADVANTAGE OF THE INVENTION According to this invention, durability of the insertion ring arrange | positioned between a 1st external gear and a 2nd external gear can be improved more.

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. Sectional view along the line II-II in FIG. Sectional view along the arrow III-III line of FIG. 1 is an enlarged cross-sectional view of the main part of FIG. Further enlarged cross-sectional view of the main part of FIG. Sectional drawing equivalent to FIG. 5 which shows the principal part of the eccentric rocking | fluctuation type gear apparatus which concerns on other embodiment of this invention.

  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 an overall configuration of an eccentric oscillating gear device G according to an example of an embodiment of the present invention. 2 is a sectional view taken along the line II-II in FIG. 1, and FIG. 3 is a sectional view taken along the line III-III in FIG.

  The eccentric oscillating gear device G includes an internal gear 12, and a first external gear 114 and a second external gear 214 that are internally meshed with the internal gear 12. The first external gear 114 and the second external gear 214 are in mesh with the internal gear 12 while being swung by the three crankshafts 28. The insertion ring 20 is disposed between the first external gear 114 and the second external gear 214. The first external gear 114 and the second external gear 214 have their axial positions regulated by the insertion wheel 20.

  Hereinafter, the configuration of the gear device G will be described in more detail.

  A key groove 22A is formed in the joint shaft 22 which is an input shaft of the gear device G, and the joint shaft 22 is connected to a drive shaft (not shown) via a key (not shown). An input pinion 24 is formed at the tip of the joint shaft 22. The input pinion 24 meshes simultaneously with the three sorting gears 26.

  The gear device G has three crankshafts 28 for oscillating the first external gear 114 and the second external gear 214 at positions offset from the axis C12 of the internal gear 12. The three sorting gears 26 are integrated with each crankshaft 28.

  The crankshaft 28 has a first eccentric body 130 and a second eccentric body 230 on both axial sides of the sorting gear 26. The first eccentric body 130 and the second eccentric body 230 have a first axis C130 and a second axis C230 that are eccentric with respect to the axis C28 of the crankshaft 28 by an eccentric amount e, respectively. The first eccentric bodies 130 of each crankshaft 28 have the same eccentric phase, and the second eccentric bodies 230 of each crankshaft 28 have the same eccentric phase. The eccentric phase difference between the first eccentric body 130 and the second eccentric body 230 is 180 degrees (eccentric in a direction away from each other).

  The first external gear 114 and the second external gear 214 are incorporated in the first eccentric body 130 and the second eccentric body 230 via the first eccentric body bearing 132 and the second eccentric body bearing 232, respectively. The first external gear 114 and the second external gear 214 can swing with respect to the axis C12 of the internal gear 12 (within a range of ± e), and both are internally meshed with the internal gear 12. ing.

  Specific configurations such as the shapes of the first external gear 114 and the second external gear 214 will be described in detail later.

  In the gear device G, the internal gear 12 includes an internal gear main body 12A integrated with the casing 36, an external pin groove 12B formed on the inner periphery of the internal gear main body 12A, and the external pin groove 12B. And an outer pin 12C supported rotatably. The outer pin groove 12B has a semicircular cross section perpendicular to the shaft, and is formed along the axial direction on the inner periphery of the internal gear body 12A. The outer pin 12 </ b> C constitutes an inner tooth of the internal gear 12.

  The number of internal teeth of the internal gear 12 (the number of external pins 12C) is slightly smaller than the number of external teeth 114A1, 214A1 of the first external gear 114 and the second external gear 214 (2 in this gear device G). Only) Many.

  A first carrier 138 and a second carrier 238 are disposed on both sides in the axial direction of the first external gear 114 and the second external gear 214. The three crankshafts 28 are supported by the first carrier 138 and the second carrier 238 via the first crankshaft bearing 140 and the second crankshaft bearing 240, respectively. In the gear device G, the first crankshaft bearing 140 and the second crankshaft bearing 240 are constituted by roller bearings having first rollers 140A and second rollers 240A. The first crankshaft bearing 140 and the second crankshaft bearing 240 do not have dedicated inner and outer rings, the crankshaft 28 also functions as an inner ring, and the first carrier 138 and the second carrier 238 function as an outer ring. Is also used.

  The first carrier 138 and the second carrier 238 are supported by the casing 36 via the first main bearing 143 and the second main bearing 243. In the gear device G, the first main bearing 143 is constituted by an angular ball bearing having a first ball 143A and a first outer ring 143B. The second main bearing 243 is composed of an angular ball bearing having a second ball 243A and a second outer ring 243B. The first main bearing 143 and the second main bearing 243 do not have an inner ring, and the first carrier 138 and the second carrier 238 also function as the inner ring. Reference numeral 55 denotes a spacer, and reference numeral 56 denotes a shim for adjusting the preload of the first main bearing 143 and the second main bearing 243.

  The first carrier 138 and the second carrier 238 are connected via a connection block 44. Specifically, three connection blocks 44 are integrally projected from the second carrier 238. The distal end 44A of the connection block 44 is in contact with the first carrier 138, and a knock pin 45 and a bolt 46 are screwed into the connection block 44 from the side opposite to the second carrier of the first carrier 138. The first carrier 138 and the second carrier 238 are connected via a connecting block 44 to constitute a carrier body that rotates integrally.

  A flange portion 36 </ b> A is formed on the outer periphery of the casing 36. The flange portion 36A is formed with a connection hole 36B for connecting the casing 36 to a first mating member (not shown). A connection hole 238 </ b> F for connecting the second carrier 238 to a second mating member (not shown) is formed on the end surface of the second carrier 238 on the side opposite to the second external gear. As the joint shaft (input shaft) 22 rotates, the second mating member coupled to the second carrier 238 rotates relative to the first mating member coupled to the casing 36. An oil seal 48 is disposed between the second carrier 238 and the casing 36.

  Here, with reference mainly to FIGS. 1, 4, and 5, the configuration in which the axial positions of the first external gear 114 and the second external gear 214 are regulated by the insertion wheel 20 will be described in detail. 4 is an enlarged cross-sectional view of a main part of FIG. 1, and FIG. 5 is an enlarged cross-sectional view of a further main part of FIG.

  In the gear device G, the insertion ring 20 is disposed between the first external gear 114 and the second external gear 214. As shown in FIG. 1, the first external gear 114, the insertion wheel 20, and the second external gear 214 are cross-sections including the axis C <b> 12 of the internal gear 12 (FIGS. 1, 4, and 5 In the cross section), the axial center AC20 of the insertion wheel 20 and the axis C12 of the internal gear 12 intersect with each other at a point P1.

  The first external gear 114, the second external gear 214, and the insertion ring 20 are all linear with respect to the axial centers AC114, AC214, and AC20 on the surface including the axis C12 of the internal gear 12. It has a symmetric configuration. Therefore, the configurations (relationships) of the first external gear 114 and the insertion wheel 20 are the same as the configurations (relationships) of the second external gear 214 and the insertion wheel 20.

  Therefore, in the following, the description will be given mainly focusing on the configuration of the first external gear 114 on the axial insertion wheel 20 side and the configuration of the insertion wheel 20 on the axial first external gear 114 side, and overlapping description will be given. Are omitted as appropriate.

  The first external gear 114 is provided at a tooth portion 114A having an external tooth 114A1 that meshes with an internal tooth (external pin 12C) of the internal gear 12, and an end portion of the tooth portion 114A on the second external gear 214 side. The tooth chamfered portion 114B is provided, and a gear side abutting surface 114C that is provided on the radially inner side of the tooth chamfered portion 114B and abuts against the insertion wheel 20.

  As shown in FIG. 5, the chamfered portion 114 </ b> B of the first external gear 114 has an end portion of the tooth portion 114 </ b> A of the first external gear 114 perpendicular to the axis C <b> 114 of the first external gear 114. It is constituted by a chamfered surface cut at an angle inclined by θ1 from the surface.

  A gear-side contact surface 114C of the first external gear 114 is a surface with which a later-described insert wheel-side contact surface 20C of the insert wheel 20 contacts, and is formed on the radially inner side of the tooth chamfered portion 114B. The gear-side contact surface 114 </ b> C is configured by a plane perpendicular to the axis C <b> 114 of the first external gear 114, and is subjected to a polishing process in order to maintain good sliding with the insertion wheel 20.

  In the gear device G, the first external gear 114 is further separated from the gear wheel 20 by moving further away from the gear wheel 20 than the gear side contact surface 114C, on the radially inner side of the gear side contact surface 114C. It has an escape portion 114D that does not abut. The escape portion 114D is continuous to the radially inner side of the gear-side contact surface 114C, and moves away from the gear-side contact surface 114C in the axial direction toward the side opposite to the counter wheel, and further radially inward from the separation surface 114D1. It has a rough end surface 114D2 that is continuous and parallel to the gear-side contact surface 114C (perpendicular to the axis C114 of the first external gear 114). Since the separation surface 114D1 and the rough end surface 114D2 of the escape portion 114D do not come into contact with the feed wheel 20, the polishing process is not performed. That is, the rough end surface 114D2 is rougher than the gear-side contact surface 114C.

  In this gear device G, since the tooth chamfered portion 114B is inclined by θ1 from the gear side contact surface 114C perpendicular to the axis C114 of the first external gear 114, the tooth chamfered portion 114B and the gear side chamfer A gear side outer corner 114P is formed between the contact surfaces 114C. In addition, the gear side contact surface 114C and the relief portion are provided on the radially inner side of the gear side contact surface 114C. A gear side inner corner 114Q is formed between the first gear 114D and the gear 114D.

  On the other hand, the insertion wheel 20 is disposed between the first external gear 114 and the second external gear 214. The first external gear 114 and the second external gear 214 are arranged between the first outer ring 143B of the first main bearing 143 and the second outer ring 243B of the second main bearing 243 with the insertion ring 20 interposed therebetween. The movement in the axial direction is restricted by being sandwiched together with the spacer 55 and the shim 56.

  The crankshaft 28 is restrained in the axial position by the first carrier 138 and the second carrier 238 via the first washer 150 and the second washer 250.

  The entire insertion ring 20 is formed in a ring shape, and the cross-sectional shape including the axis C12 of the internal gear 12 is substantially rectangular. The insertion ring 20 has an outer peripheral surface 20A and an inner peripheral surface 20B that are parallel to the axis C12 of the internal gear 12, and is perpendicular to the axis C12 of the internal gear 12 with the outer peripheral surface 20A and the inner peripheral surface 20B interposed therebetween. Have two contact wheel side contact surfaces 20C and 20D. The insertion wheel side contact surface 20C contacts the gear side contact surface 114C of the first external gear 114, and the insertion wheel side contact surface 20D contacts the gear side contact surface 214C of the second external gear 214. Touch.

  On the side of the first external gear 114 of the insertion wheel 20, a corner between the outer peripheral surface 20 </ b> A and the insertion wheel side contact surface 20 </ b> C is provided on the insertion wheel side outer chamfered portion 20 </ b> G, and the inner peripheral surface 20 </ b> B and the insertion wheel side contact surface. An insertion wheel side inner surface chamfer 20H is formed at the corner between 20C. On the second external gear 214 side, the corner between the outer peripheral surface 20A and the insertion wheel side contact surface 20D is located at the outer side chamfer 20J, and the inner peripheral surface 20B and the insertion wheel side contact surface 20D. An insertion wheel side inner surface chamfer 20K is formed at each corner.

  In this gear device G, the gear-side outer corner 114P, which is the corner between the tooth chamfer 114B and the gear-side contact surface 114C of the first external gear 114, is placed on the side of the sprocket wheel over the entire circumference. In this example, δL (114P-20Q) is located on the radially outer side with respect to the shaft center C12 of the internal gear 12 relative to the inner ring side corner portion 20Q which is a corner portion on the inner diameter side of the contact surface 20C. Yes. Here, the insertion wheel side inner corner portion 20Q, which is a corner portion on the inner diameter side of the insertion wheel side contact surface 20C, refers to the inner peripheral edge of the same plane as the insertion wheel side contact surface 20C. In this example, it corresponds to the corner between the insertion wheel side contact surface 20C and the insertion wheel side inner surface chamfer 20H. The same is true for the rear insertion wheel side inner corner 80Q.

  In other words, regardless of the swinging state of the first external gear 114, the insertion wheel side inner corner portion 20Q is always more than the gear side outer corner portion 114P than the shaft center C12 of the internal gear 12. Is located radially inward.

  This is because the radius from the axis C12 of the internal gear 12 (= the axis C20 of the insert wheel 20) to the insert wheel side inner corner 20Q is R20Q, and the gear side outer angle from the axis C12 of the internal gear 12 is shown. This also means that the minimum distance Ls114P to the portion 114P is larger than the radius R20Q (Ls114P> R20Q).

  In other words, if the radius from the axis C114 of the first external gear 114 to the gear-side outer corner 114P is R114P, the minimum from the axis C12 of the internal gear 12 to the gear-side outer corner 114P is the minimum. Since the distance Ls114P can be expressed as (R114P-e), it can be understood that the relationship of (R114P-e)> R20Q is established.

  In this gear device G, the outer peripheral surface 20 </ b> A of the insertion wheel 20 is in contact with the outer pin 12 </ b> C constituting the internal teeth of the internal gear 12. That is, the outer diameter of the outer peripheral surface 20A of the insertion wheel 20 is equal to the inscribed circle diameter of the outer pin 12C.

  As described above, in this gear device G, the same configuration as that between the insertion wheel 20 and the first external gear 114 is also applied between the insertion wheel 20 and the second external gear 214. Have.

  Therefore, in the present specification, the first two external gears 114 have the same reference numerals in the 100s and the second external gear 214 has the same last two digits in the 200s, and the suffixes at the end are distinguished from uppercase and lowercase letters. As a result, the externally inserted gears 114 and 214 are made to correspond to the axially inserted wheel side and the oppositely inserted wheel side. For the insert wheel 20, the insert wheel side contact surfaces 20C and 20D, the insert wheel side outer chamfered portions 20G and 20J, the insert wheel side inner chamfered portions 20H and 20K, the insert wheel side outer corner portions 20P and 20S, and the insert wheel side inner side The corners 20Q and 20R correspond to each other. Therefore, the code | symbol corresponding to the site | part corresponding only to drawing is attached | subjected, and duplication description may be abbreviate | omitted in the specification.

  Next, the operation of the gear device G will be described.

  When the joint shaft 22 is rotated by rotation of a drive shaft (not shown), the three sorting gears 26 are rotated in the same direction and at the same speed via the input pinion 24. As a result, the three crankshafts 28 rotate at the same speed in the same direction.

  When the first eccentric body 130 of each crankshaft 28 rotates in synchronization, the first external gear 114 swings via the first eccentric body bearing 132. In addition, the second eccentric body 230 of each crankshaft 28 rotates in synchronization with each other, so that the second external gear 214 swings through the second eccentric body bearing 232. Since the eccentric phase of the first eccentric body 130 and the second eccentric body 230 is shifted by 180 degrees (being eccentric in a direction away from each other), the first external gear 114 and the second external gear 214 are also mutually It swings while being eccentric in the direction of separation.

  The first external gear 114 and the second external gear 214 are in mesh with the internal gear 12, respectively. Since the number of internal teeth (external pins 12C) of the internal gear 12 is two more than the number of external teeth 114A1, 214A1 of the first external gear 114 and the second external gear 214, the first external gear 114 is provided. Each time the second external gear 214 swings once, the first external gear 114 and the second external gear 214 rotate relative to the internal gear 12 by an amount corresponding to a difference in the number of teeth. (Rotate).

  As the first external gear 114 and the second external gear 214 rotate, the three crankshafts 28 slowly revolve around the axis C12 of the internal gear 12. When the crankshaft 28 revolves around the axis C12 of the internal gear 12, the first carrier 138 and the second carrier 138 supporting the crankshaft 28 via the first crankshaft bearing 140 and the second crankshaft bearing 240 are used. The carrier 238 rotates around the axis C <b> 12 of the internal gear 12.

  The power transmitted to the first carrier 138 side merges with the power transmitted to the second carrier 238 side via the connection block 44. As a result, the second mating member coupled to the second carrier 238 can be rotated with respect to the first mating member coupled to the casing 36.

  Here, in this gear device G, the gear side outer corner 114P, which is a corner between the tooth chamfered portion 114B of the first external gear 114 and the gear side contact surface 114C, extends over the entire circumference. It is located on the outer side in the radial direction with respect to the inner side corner portion 20Q which is the inner diameter side corner portion of the insertion wheel side contact surface 20C. In other words, no matter what the first external gear 114 is in a swinging state (even if the gear-side outer corner 114P of the first external gear 114 is closest to the axis C12 of the internal gear 12). However, the insertion wheel side inner corner portion 20Q is always located radially inward from the gear side outer corner portion 114P.

  Therefore, the insertion wheel side contact surface 20C of the insertion wheel 20 always comes into contact with the gear side contact surface 114C (a flat portion thereof). That is, when the gear-side outer corner 114P is swayed more radially outward from the state closest to the axis C12 of the internal gear 12 (that is, from the axis C12 of the internal gear 12). When the distance to the gear-side outer corner 114P increases from the state where the minimum distance Ls114P is reached), the gear-side outer corner 114P does not collide with the wheel-side inner corner 20Q. Therefore, damage to the insertion wheel 20 is suppressed.

  In addition, even when the first external gear 114 is in any swinging state, the insertion wheel 20 is always in contact with the gear-side contact surface 114C of the axial first external gear 114. In order to maintain, tilting of the axis C20 is also suppressed, and the behavior is stabilized. Therefore, the position restriction of the first external gear 114 in the axial direction can be performed more stably, and as a result, the radial support of the outer pin 12C on the outer peripheral surface 20A can be performed more stably.

  Further, in the present gear device G, the following operation is also obtained.

  In this gear device G, the internal gear 12 is rotatably supported by the internal gear main body 12A, the outer pin groove 12B formed on the inner periphery of the internal gear main body 12A, and the outer pin groove 12B. An outer pin 12C is provided, and an outer peripheral surface 20A of the insertion wheel 20 is in contact with the outer pin 12C. For this reason, the insertion ring 20 not only restricts the axial positions of the first external gear 114 and the second external gear 214 but also supports the outer pin 12C from the radially inner side. Accordingly, it is possible to effectively prevent the outer pin 12C from falling off the outer pin groove 12B without providing a separate support means.

  Further, in the present gear device G, the first external gear 114 is disposed on the radially inner side of the gear-side contact surface 114C (by moving away from the wheel 20 than the gear-side contact surface 114C). 114D has an escape portion 114D that does not abut. The gear-side contact surface 114C needs to be polished in order to maintain good sliding with the insertion wheel 20, but this configuration can reduce the polishing area and reduce the processing time and processing cost. it can.

  In this gear device G, the first external gear 114 and the second external gear 214 have the same configuration, and the insert ring 20 has the same configuration also on the second external gear 214 side. Have the same effect.

  FIG. 6 shows a configuration example according to another embodiment of the present invention.

  6 is different from the insertion wheel 20 of the previous embodiment only in the insertion wheel 80, and other configurations including the first external gear 114 and the second external gear 214 are as follows. This is the same as the previous embodiment. Therefore, the members other than the insertion wheel 80 are denoted by the same reference numerals as those of the previous embodiment, and the insertion wheel 80 is provided in a portion corresponding to the insertion wheel 20 of the previous embodiment. The same subscripts as those used in the embodiment will be given, and repeated explanation will be omitted as appropriate.

  6 is formed in a ring shape as a whole, and has an outer peripheral surface 80A and an inner peripheral surface 80B parallel to the axis C12 of the internal gear 12, and the axis C12 of the internal gear 12. Two contact wheel side contact surfaces 80C and 80D that are perpendicular to each other. The insertion wheel side contact surface 80C contacts the gear side contact surface 114C of the first external gear 114, and the insertion wheel side contact surface 80D contacts the gear side contact surface 214C of the second external gear 214. Touch.

  Further, on the first external gear 114 side of the insertion wheel 80, the insertion wheel side outer chamfered portion 80G and the inner peripheral surface 80B are contacted with the insertion wheel side at the corners between the outer peripheral surface 80A and the insertion wheel side contact surface 80C. An insertion wheel side inner surface chamfered portion 80H is formed at a corner between the surfaces 80C. Also on the second external gear 214 side, the outer side chamfered portion 80J is formed at the corner between the outer peripheral surface 80A and the insertion wheel side contact surface 80D, and the inner peripheral surface 80B and the insertion wheel side contact surface 80D. An insertion wheel side inner surface chamfer 80K is formed at each corner.

  However, for example, the insertion wheel side outer chamfered portion 80G is larger than the previous embodiment, and in particular, the radial length L80G is 2.5 times or more larger than the axial width W80G. As a result, the insertion wheel side outer corner portion 80P, which is a corner portion between the insertion wheel side outer chamfered portion 80G and the insertion wheel side contact surface 80C, has a radial length L80G with respect to the outer peripheral surface 80A of the insertion wheel 80. It is shifted to the inner diameter side by a large amount. Here, the insertion wheel side outer corner portion 80P, which is a corner portion between the insertion wheel side outer chamfered portion 80G and the insertion wheel side contact surface 80C, is the outer periphery of the same plane as the insertion wheel side contact surface 80C. Pointing to the edge.

  With the gear wheel side outer chamfered portion 80G having such a configuration, in the gear device G, the gear side outer corner portion which is a corner portion between the tooth portion chamfered portion 114B and the gear side contact surface 114C. 114P is more than δL (114P-80P) of the internal gear 12 shaft than the insertion-wheel-side outer corner portion 80P, which is the outer-diameter-side corner portion of the insertion-wheel-side contact surface 80C, over the entire circumference. It is located radially outside the center C12.

  Therefore, the gear-side outer corner portion 114P of the first external gear 114 is not in contact with the insertion wheel-side inner corner portion 80Q (not only in contact with the insertion wheel-side inner corner portion 80Q), and makes contact with the insertion wheel 80 at all. There is nothing. In other words, the insertion wheel side contact surface 80C is completely in contact with only the flat portion of the gear side contact surface 114C, and wear of the insertion wheel 80 can be further reduced.

  The configuration in which the insertion wheel side outer chamfered portion 80G is provided is as follows. It can also be understood as “having”. In other words, the insertion wheel side outer chamfered portion 80G that functions as the non-contact surface does not necessarily have to be linear as in this example, and may be curved or stepped. Also good.

  Further, in this gear device G, the gear-side inner corner 114Q, which is a corner between the gear-side abutment surface 114C and the relief portion 114D, has an outer diameter over the entire circumference. It is located radially inward with respect to the axial center C12 of the internal gear 12 with respect to the insertion wheel side outer corner portion 80P which is a corner portion on the side.

  Since this configuration is easier to understand on the second external gear 214 side, for convenience, the description will be given with reference to the second external gear 214 side. The gear-side inner corner portion 214Q, which is the corner portion between the two, is an internal gear over the entire circumference of the gear wheel-side outer corner portion 80S that is the corner portion on the outer diameter side of the wheel-side contact surface 80D. With respect to the twelve axis C12, it can be replaced with a configuration in which δL (80S-214Q) is located on the radially inner side.

  In this configuration, the maximum distance Lm214Q from the axis C12 of the internal gear 12 to the gear side inner corner 214Q is smaller than the radius R80S from the axis C12 of the internal gear 12 to the outer ring side corner 80S. In other words, (Lm214Q <R80S).

  In other words, the maximum distance Lm214Q to the gear-side inner corner 214Q is expressed by using a radius R214Q from the axis C214 of the second external gear 214 to the gear-side inner corner 214Q. (R214Q + e) Therefore, it can be understood that the relationship of (R214Q + e) <R80S is established.

  By adopting this configuration, the gear-side inner corner portion 214Q is always positioned radially inward from the gear wheel-side outer corner portion 80S regardless of the swinging state of the second external gear 214. The effect is obtained. As a result, in particular, the gear side outer corner portion 214P is moved more radially inward from a state where the gear side outer corner portion 214P is moved away from the axis C12 of the internal gear 12 (a swinging state like the second external gear 214 in FIG. 6). When attempting to swing, it is possible to prevent the gear side inner corner portion 214Q from colliding with the insertion wheel side outer corner portion 80S. This effect is also obtained on the first external gear 114 side.

  After all, by adding this configuration, the first external gear 114 has a tooth chamfered portion 114B on the radially outer side of the gear side contact surface 114C, and further on the radially inner side of the gear side contact surface 114C. Even when the escape portion 114D is provided, even when the first external gear 114 moves away from or closes to the axis C12 of the internal gear 12, the wear of the insertion ring 80 by the first external gear 114 is reduced. It can be reduced satisfactorily.

  In addition, this invention is applied to both the structure between a 1st external gear and an insertion ring, and the structure between a 2nd external gear and an insertion ring like the gear apparatus demonstrated until now. Although it is preferable, it may be applied to only one of them.

  In the gear device, the first external gear and the second external gear are configured symmetrically with respect to the respective axial centers. However, the first external gear and the second external gear are: It is not always necessary to form it symmetrically with respect to the axial center. For example, it is sufficient that the tooth chamfered portion is provided at least at the end portion on the second external gear side (insertion wheel side).

  In the above gear device, the eccentric oscillating gear device is an eccentric oscillating gear device called a so-called sort type having three crankshafts at a position offset from the axis of the internal gear. Was adopted. However, a gear device called a so-called center crank type having one crankshaft at the axial center position of the internal gear is also known as an eccentric oscillating gear device. The present invention is also applicable to such a center crank type gear device.

  In the above gear device, an eccentric oscillating gear device having two external gears of a first external gear and a second external gear has been shown. The gear device having three sheets can be similarly applied to the insertion ring between the external gears, and the same operational effects can be obtained.

  ADVANTAGE OF THE INVENTION According to this invention, durability of the insertion ring arrange | positioned between a 1st external gear and a 2nd external gear can be improved more.

G: Eccentric oscillating gear device 12: Internal gear 114 ... First external gear 114A1 ... External tooth 114A ... Tooth portion 114B ... Tooth chamfered portion 114C ... Gear-side contact surface 114P ... Gear-side outer corner 114Q ... Gear side inner corner 214 ... Second external gear 20 ... Insert wheel 20C ... Insert wheel contact surface 20Q ... Insert wheel side inner corner 28 ... Crankshaft

Claims (6)

An internal gear, a first external gear and a second external gear internally meshing with the internal gear, a crankshaft for swinging the first external gear and the second external gear, and the first In an eccentric oscillating gear device comprising an external gear and an insertion wheel disposed between the second external gear,
The first external gear includes a tooth portion having external teeth that mesh with internal teeth of the internal gear, and a tooth chamfered portion provided at an end of at least the second external gear side of the tooth portion. A gear-side contact surface that is provided on the radially inner side of the tooth chamfered portion and contacts the insertion wheel,
The insertion wheel has an insertion wheel side contact surface that contacts the gear side contact surface,
The corner between the tooth chamfered portion of the first external gear and the gear-side contact surface is more than the inner tooth than the corner on the inner diameter side of the contact wheel-side contact surface over the entire circumference. An eccentric oscillating gear device, wherein the gear device is positioned radially outward with respect to the shaft center of the gear. The eccentric oscillating gear device according to claim 1,
The corner between the chamfered portion of the tooth portion and the contact surface on the gear side has an entire circumference with respect to the axial center of the internal gear rather than the corner portion on the outer diameter side of the contact surface on the sprocket wheel side. An eccentric oscillating gear device characterized by being positioned radially outward. The eccentric oscillating gear device according to claim 1 or 2,
The internal gear has an internal gear main body, an external pin groove formed on the inner periphery of the internal gear main body, and an external pin rotatably supported by the external pin groove,
An eccentric oscillating gear device, wherein an outer periphery of the insertion ring abuts on the outer pin. In the eccentric rocking | fluctuation type gear apparatus in any one of Claims 1-3,
The eccentric wheel gear device characterized in that the insertion wheel has a non-contact surface that does not contact the first external gear on the radially outer side of the contact surface on the insertion wheel side. In the eccentric rocking | fluctuation type gear apparatus in any one of Claims 1-4,
The first external gear has an escape portion that does not come into contact with the insertion wheel on the radially inner side of the gear-side contact surface. The eccentric oscillating gear device according to claim 5,
The corner between the gear-side contact surface and the relief portion has a diameter with respect to the shaft center of the internal gear over the entire circumference rather than the corner on the outer diameter side of the insertion wheel-side contact surface. An eccentric oscillating gear device, characterized in that it is located on the inner side in the direction.

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