JP2013194869A - Eccentric oscillating reduction gear, and method for manufacturing external gear for the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an eccentric oscillating reduction gear allowing production of external gears in a shorter time and at lower cost.SOLUTION: An eccentric oscillating reduction gear G1 includes: external gears 12, 14; an internal gear 16 inscribed while the external gears 12, 14 oscillate; and an inner roller (pin-shaped member) 38 inserted into through-holes 34, 36 formed in the external gears 12, 14, brought into contact with inner peripheries of the through-holes 34, 36, and synchronizing with rotational components of the external gears 12, 14. In the eccentric oscillating reduction gear G1, the through-holes 34, 36 have nonuniform inner diameters in an axial direction.

Description

  The present invention relates to an eccentric oscillating speed reducer and a method for manufacturing the external gear.

  For example, Patent Document 1 discloses an eccentric oscillating speed reducer.

  The reduction gear includes an external gear and an internal gear that is inscribed while the external gear swings. The external gear is swung by an eccentric body provided on the input shaft. The external gear is provided with a plurality of through holes, and pin-like members (inner pins and inner rollers) are inserted therein. The pin-like member is fixed or fitted to the flange portion of the output shaft. For this reason, the pin-shaped member is synchronized with the rotation component of the external gear.

  The external gear has a number of external teeth that is slightly smaller than the number of internal teeth of the internal gear.

  In this configuration, when the input shaft rotates, the external gear swings while being in mesh with the internal gear, and rotates relative to the internal gear (rotates). This rotation component is taken out from the output shaft through sliding of the through hole provided in the external gear and the pin-shaped member inserted into the through hole, thereby obtaining a rotation reduced from the output shaft.

JP 2000-249199 A

  In this type of eccentric oscillating speed reducer, a large number of through holes into which pin-like members for taking out the rotation of the external gear (or for constraining the rotation) are inserted are formed. There is a need to. The more the smoothness and the higher hardness are required for the through hole, the higher the slidability and the long life with the pin-like member are required.

  Therefore, it takes time and cost to form the through hole, which is a major factor in increasing the manufacturing cost of the external gear.

  The present invention has been made in order to solve such problems, and provides an eccentric oscillating type speed reducer that can manufacture an external gear in a shorter time and at a lower cost. That is the issue.

  The present invention is inserted into an external gear, an internal gear that is inscribed while the external gear swings, and a through hole provided in the external gear, and contacts the inner periphery of the through hole to In the eccentric oscillating type speed reducer provided with a pin-like member that synchronizes with the rotation component of the external gear, the above-mentioned problem has been solved by adopting a configuration in which the inner diameter of the through hole is not uniform in the axial direction. Is.

  In the present invention, the through holes that have been formed with a uniform inner diameter over the entire length in the axial direction of the external gear as a matter of course are intentionally formed non-uniformly. This intention is based on the knowledge to be described later, and the function of the original “through hole” that truly contributes to power transmission is assigned to only a part of the inner peripheral surface in the axial direction, and the other part has the function. It is to avoid having. As a result, time-consuming and costly through-holes, in particular, finishing can be performed only in a part of the axial direction, thereby reducing the time and cost for forming the through-holes. it can.

  Note that the present invention can be understood from the viewpoint of a manufacturing method of an external gear: "External gear, internal gear that is inscribed while the external gear swings, and a through-hole provided in the external gear. In the manufacturing method of the external gear of the eccentric oscillating speed reducer, the pin-shaped member inserted into the hole and in contact with the inner periphery of the through-hole to synchronize with the rotation component of the external gear, A step of forming a through hole in the material of the external gear, a step of forming an inner diameter of a part of the through hole in an axial direction, and a step of increasing the diameter of the part. And a step of hardening the material of the external gear, and a step of finishing a portion of the raw hole that has not been made large diameter after the hardening treatment. It can also be understood as “a manufacturing method of an external gear of a type reduction gear”.

  ADVANTAGE OF THE INVENTION According to this invention, the eccentric rocking | swiveling type reduction gear which can manufacture an external gear in a shorter time and at lower cost can be obtained.

The expanded sectional view which shows the principal part of the eccentric rocking | fluctuation type reduction gear which concerns on an example of embodiment of this invention Sectional drawing of the principal part of the gearmotor to which the reduction gear concerning the said embodiment is applied Sectional view along the line III-III of FIG. Manufacturing process diagram of external gear of eccentric rocking type reduction gear according to the above embodiment The expanded sectional view of the through-hole vicinity of the external gear which concerns on the modification (other embodiment) of the said embodiment Enlarged sectional view corresponding to FIG. 5 according to another modification of the above embodiment FIG. 5 is an enlarged cross-sectional view corresponding to FIG. 5 according to another modification of the embodiment. FIG. 5 is an enlarged cross-sectional view corresponding to FIG. 5 according to another modification of the embodiment.

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

  1 to 3 show a gear motor to which an eccentric oscillating speed reducer according to an example of an embodiment of the present invention is applied.

  The gear motor GM1 is obtained by integrally connecting a motor M1 and an eccentric oscillating speed reducer G1. The eccentric oscillating speed reducer G1 includes external gears 12 and 14 and an internal gear 16 that is inscribed while the external gears 12 and 14 swing, and the external gears 12 and 14 and the internal gears. 16 is extracted as an output.

  The motor shaft 18 of the motor M1 also serves as the input shaft 20 of the reduction gear G1. A cylindrical member 25 is fitted to the input shaft 20 via a key 21. As shown in FIG. 1, two eccentric bodies 22 and 24 are formed on the tubular member 25 with a predetermined phase difference (180 degrees in this example). The shafts of the eccentric bodies 22 and 24 are each eccentric by δe with respect to the shaft center O1 of the input shaft 20. Two external gears 12 and 14 are attached to the eccentric bodies 22 and 24 via roller bearings 26 and 28 and eccentric body shaft holes 30 and 32, respectively.

  Each external gear 12, 14 has a plurality of through holes 34, 36 (eight in this example: see FIG. 3). An inner pin 40 covered with an inner roller 38 is inserted into the through holes 34 and 36.

  The outer diameter d1 of the inner roller 38 is smaller than the inner diameter D1 of the through holes 34 and 36 (the inner diameter of a constant diameter portion 34B having a uniform inner diameter described later) D1 by twice the eccentric amount δe (a gap corresponding to 2 · δe). S1 is present). The inner pin 38 is covered with the inner roller 38 because the slip between the original inner pin 40 and the external gears 12 and 14 is “between the inner pin 40 and the inner periphery of the inner roller 38” and “inner This is because a smoother sliding characteristic is obtained by dispersing between the outer periphery of the roller 38 and the through holes 34 and 36.

  When the inner roller 38 is covered on the inner pin 40 as in the present embodiment, the inner roller 38 corresponds to “a pin-shaped member that contacts the through-hole of the external gear”. It may be understood that it constitutes a “pin-shaped member” (when the inner roller is not covered, the inner pin itself constitutes “a pin-shaped member that contacts the through-hole of the external gear”). Since the inner roller 38 is inserted into the through holes 34 and 36 of the external gears 12 and 14 and is in contact with the inner periphery of the through holes 34 and 36, it synchronizes with the rotation component of the external gears 12 and 14. Make a move. The configuration of the through holes 34 and 36 will be described in detail later.

  The inner pin 40 is press-fitted and fixed to the flange portion 42 </ b> A of the output shaft 42.

  The two external gears 12 and 14 are provided mainly for the purpose of increasing the transmission capacity and maintaining the rotational balance by changing the eccentric phase. On the outer periphery of the external gears 12 and 14, trochoidal external teeth 12A and 14A are provided.

  In this embodiment, the internal gear 16 is integrated with the casing 50 and fixed in an internal gear main body 16A, and is supported by the internal gear main body 16A and an external pin 16B constituting the internal teeth of the internal gear 16. And an outer roller 16C which is rotatably covered on the outer pin 16B.

  In this embodiment, the number of external teeth of the external gears 12 and 14 is “21”, and the number of internal teeth of the internal gear 16 (the number of external pins 16B and external rollers 16C) is “22”. is there. That is, the number of external teeth of the external gears 12 and 14 is slightly smaller (by 1 in this example) than the number of internal teeth of the internal gear 16.

  Here, before entering into a specific description of the configuration of the through holes 34, 36 of the external gears 12, 14, in order to make the present embodiment easier to understand, the eccentric oscillating speed reducer G1 is described. The operation of the power transmission system will be briefly described.

  When the input shaft 20 integrated with the motor shaft 18 is rotated once by the rotation of the motor shaft 18 of the motor M1, eccentric bodies 22 and 24 formed on the cylindrical member 25 connected to the input shaft 20 are rotated. Rotates once. When the eccentric bodies 22 and 24 rotate, the external gears 12 and 14 oscillate while internally meshing with the internal gear 16 via the roller bearings 26 and 28.

  Since the external gears 12 and 14 and the internal gear 16 have a difference in the number of teeth of “1”, the external gears 12 and 14 are in a fixed state each time the input shaft 20 rotates once. 16, the phase in the circumferential direction is shifted (rotates) by an amount corresponding to the difference in the number of teeth “1”. This rotation component is transmitted to the flange portion 42 </ b> A of the output shaft 42 via the inner roller 38 and the inner pin 40 inserted into the through holes 34 and 36. As a result, the output shaft 42 rotates at a reduced speed with a reduction ratio “1/21”. The swinging components of the external gears 12 and 14 are absorbed by the gap S1 between the inner roller 38 and the through holes 34 and 36.

  Thus, the inner roller 38 (pin-shaped member) and the through holes 34 and 36 slide while pressing with a strong force to extract the rotation component when the external gears 12 and 14 swing. Yes. Therefore, in order to ensure the strength and hardness required for the through holes 34 and 36, hardened materials that are quenched are used for the external gears 12 and 14. In other words, this is a time-consuming and costly finishing process for the through holes 34 and 36 formed in the hard material, such as cutting with a carbide tool or grinding (or honing) with an extremely hard grindstone. Means you have to do.

  On the other hand, the through holes 34 and 36 are important components that play a central role in the power transmission system of the eccentric oscillating speed reducer G1. It was precisely formed with a uniform inner diameter over the entire length Lt (in other words, it was understood that it was necessary to form with a uniform inner diameter and precisely over the entire length Lt). Therefore, conventionally, it has been a major factor in increasing the cost of the external gears 12 and 14.

  However, when the inventor examines again, the contact between the through holes 34 and 36 and the inner roller 38 is a contact between the concave surface and the convex surface. Therefore, for example, contact between the external gears 12 and 14 and the internal gear 16 (the outer roller 16C), or contact between the convex surfaces and the convex surfaces such as contact between the eccentric bodies 22 and 24 and the bearings 26 and 28. Rather, the surface pressure is low. Further, even when compared with the contact between the eccentric body shaft holes 30 and 32 where the same concave surface and convex surface are in contact with the bearings 26 and 28, the diameter difference between the concave surface and convex surface is small, which is advantageous in terms of contact area. Therefore, it is relatively easy to secure lubricating oil. Therefore, in the single (same) reduction gear G1, the contact between the through-holes 34, 36 and the inner roller 38 is relatively stronger (or longer in life) than the contact of other parts. There is a margin, and the strength of the entire reduction gear G1 can be maintained (without being reduced) without necessarily securing a contact portion over the entire length Lt of the through holes 34 and 36. In the present embodiment, based on this knowledge, the through holes 34 and 36 of the external gears 12 and 14 are formed in the following configuration.

  Referring to FIG. 1, the through holes 34 and 36 of the external gears 12 and 14 according to the present embodiment are formed with an uneven inner diameter in the axial direction, and a part in the axial direction (a portion with a small inner diameter). Only is utilized for power transmission with the inner roller (pin-shaped member) 38. In addition, including the depiction of FIG. 1, the through holes 34 and 36 in each of the drawings exaggerate the change in the inner diameter so that the change in the axial direction of the inner diameter can be easily understood.

  In this embodiment, the through holes 34 and 36 have constant diameter portions 34B and 36B having an inner diameter that is uniform (constant) at D1 in the center in the axial direction. And the large diameter part which an internal diameter linearly expands to D2 is provided in the axial direction both ends of this constant diameter part 34B, 36B (D1 <D2). In this embodiment, the sum of the axial range L1 of the constant diameter portions 34B and 36B where the inner diameter of the through holes 34 and 36 is constant at D1 and the axial range L2 of the two large diameter portions 34A and 36A having a larger inner diameter. 2 · L2 is substantially the same (L1≈2 · L2). That is, in the single external gear 12 (or 14), the axial range L1 of the constant diameter portions 34B and 36B and the axial range 2 · L2 of the large diameter portion 34A (or 36A) are substantially the same. Reference numeral 54 denotes a positioning member that restricts the movement of the external gears 12 and 14 in the axial direction.

  Since the operation of this embodiment is closely related to the manufacturing process of the external gears 12 and 14, the operation of this embodiment will be described below together with the description of the method of manufacturing the through holes 34 and 36.

  Specifically, the external gear 12 having the through hole 34 is manufactured by a process as shown in FIG. 4 (the same applies to the external gear 14 having the through hole 36).

  That is, first, (a) the raw material 34R1 of the external gear 12 that has not been subjected to hardening treatment such as quenching is formed with eight uniform holes D with a uniform inner diameter D3 as a base of the through hole 34 ( FIG. 4 (A)).

  Next, (b) the inner diameter of a part (specifically, both ends in the axial direction) of each of the raw holes 34R is linearly increased so that the inner diameter increases toward the end, and both ends in the axial direction are increased. The large-diameter portion 34Ra is formed at a site in the axial direction range L6 (FIG. 4B). The process up to this point is the processing at the time when the material 12R1 of the external gear 12 has not yet been cured. Therefore, it can be performed very easily with a low-cost ordinary tool (not shown).

  In practice, a step of forming external teeth (trochoidal tooth profile) 12A on the material 12R1 of the external gear 12 before or after the step (b) is performed.

  And (c) After forming large diameter part 34Ra in all the raw holes 34R, hardening processing by hardening is performed with respect to the raw material 12R1 of the said external gear 12, and it is set as the hard raw material 12R2 (FIG.4 (C)). ). This curing process is not particularly limited to quenching, and various conventionally known curing methods can be used.

  Finally, (d) the non-large-diameter portion 34Rb of the eight raw holes 34R in which the large-diameter portions 34Ra are formed at both ends in the axial direction is uniformly finished to the inner diameter D1 (FIG. 4D). . As a result, the external gear 12 as a finished product having the constant diameter portion 34B having a uniform inner diameter D1 is obtained. The large-diameter portion 34Ra that has not been subjected to the finishing process remains as the final large-diameter portion 34A.

  Specific examples of the finishing treatment here include cutting using a carbide tool or the like, and grinding (or honing) using a grindstone composed of extremely hard and fine abrasive grains. The reason why a quenching (curing) process is performed before the finishing process is that when the quenching is performed after the finishing process, the accurate dimensions as a product cannot be maintained due to thermal distortion.

  However, in this embodiment, this finishing process is performed only on the portion of the raw hole 34R that is not made large (the portion of the constant diameter portion 34Rb having a uniform inner diameter D3) (the constant diameter portion 34B). Since the finishing process differs between the large-diameter portion 34A and the large-diameter portion 34A), the processing time is naturally shorter than when the finishing process is performed over the entire length Lt of the through holes 34 and 36 of the conventional external gear. Further, since the machining range is small, wear of the carbide tool and the like is small (the tool life is extended).

  The manufacturing cost of the external gear of this type of eccentric oscillating speed reducer has the greatest effect on the cost of finishing processing when forming a plurality of through holes (specifically, for example, the replacement cost of a carbide tip) ). Therefore, an increase in the tool life due to a small amount of processing per one external gear 12, 14 leads to a reduction in manufacturing cost of the external gear 12, 14 as it is.

  As a result, the processing time can be shortened without reducing the strength of the external gears 12 and 14 or the entire reduction gear G1, that is, while maintaining the necessary strength characteristics as the external gears 12 and 14 sufficiently. In addition, the manufacturing cost can be reduced.

  The external gears 12 and 14 according to this embodiment have large-diameter portions having an inner diameter (maximum inner diameter D2) larger than the inner diameter D1 of the constant-diameter portions 34B and 36B at the axial center of the through holes 34 and 36 at both ends in the axial direction. Since it has 34A and 36A, sliding (power transmission) with the inner roller 38 is performed at the constant-diameter portions 34B and 36B at the “axial center” of the through holes 34 and 36. Therefore, there is little possibility that a large moment or the like is generated in the engagement between the external gears 12 and 14 and the internal gear 16 or the rolling of the external gears 12 and 14 with the bearings 26 and 28.

  Further, the through holes 34 and 36 have constant diameter portions 34B and 36B having a constant inner diameter D1, and are configured so that the inner diameter expands “linearly” in the axial direction from the constant diameter portions 34B and 36B. Therefore, it is easy to process the large diameter portions 34A, 36A, and even if the external gears 12, 14 are inclined with respect to the axis O1 for some reason, the constant diameter portions 34B, It is possible to further reduce stress concentration on the axial end portions 34B1 and 36B1 of 36B.

  In the present invention, the specific shape of the inner periphery of the through-hole (change mode of the inner diameter) is not particularly limited to the above example. 5 to 8 show modified examples of the specific shape of the inner periphery of the through hole.

  In the modification shown in FIG. 5, the through holes 64 and 66 of the external gears 60 and 62 have constant diameter portions 64B and 66B having a constant inner diameter D5 at the center in the axial direction, and the constant diameter portions at both ends in the axial direction. Large diameter portions 64A and 66A are formed with a constant inner diameter D6 from 64B and 66B. In this configuration, formation of the large diameter portions 64A and 66A of the through holes 64 and 66 is easier than in the previous embodiment. Other configurations are the same as in the previous embodiment.

  In the modification shown in FIG. 6, the through-holes 74 and 76 of the external gears 70 and 72 have constant diameter portions 74B and 76B having a constant inner diameter D7, not at the center in the axial direction but at the end on the one end side in the axial direction. Have. A “single” large-diameter portion 74A, 76A is linearly expanded from the constant-diameter portions 74B, 76B to the end portion on the other end side, and the other end portion has a maximum inner diameter D8. Yes. For this reason, when forming the large diameter portions 74A and 76A, it is not necessary to replace the material of the external gears 70 and 72, and the formation process of the large diameter portions 74A and 76A can be simplified. In this modified example, the large diameter portions 74A and 76A having a larger inner diameter than the axial range L5 of the constant diameter portions 74B and 76B having a constant inner diameter D7 of the through holes 74 and 76 are formed wider. (L5 <L6). For this reason, the range L5 of the constant diameter portions 74B and 76B to be finished can be further reduced as compared with the previous two examples, and the effect of the present embodiment is obtained very remarkably.

  In addition, as shown in the modified example of FIG. 6, as a result of suppressing the axial range L5 of the constant diameter portions 74B and 76B to be finished to a small size, the constant diameter portions 74B and 76B of the through holes 74 and 76 and the inner rollers ( When the maximum surface pressure P1 between the inner gear 16 and the external gears 70 and 72 increases, for example, the maximum surface pressure P1 between the inner gear 16 and the external gears 70 and 72 increases. There is. However, even in such a situation (P1> P2), this rarely becomes a bottleneck on the strength or life of the reduction gear G1 (sufficiently the entire reduction gear G1 so far). Strength or lifetime can still be maintained). This is because the contact portions between the constant diameter portions 74B and 76B of the through holes 74 and 76 and the inner roller 38 have better lubricity and higher processing accuracy than the contact portions of the internal gear 16 and the external gears 70 and 72. It is.

  In the modification shown in FIG. 7, the reduction in strength in the vicinity of the through holes 84 and 86 of the external gears 80 and 82 is minimized by suppressing the range of the large diameter portions 84A and 86A to be relatively small. Yes. For example, when the axial width L7 of the external gears 80, 82 is not originally set so large, the axial range L8 of the large diameter portions 84A, 86A is thus changed to the axial range of the constant diameter portions 84B, 86B. You may make it form smaller than L9. Nevertheless, as long as the large-diameter portions 84A and 86A are formed even slightly, it is possible to obtain the effects of time reduction and cost reduction.

  In the modification of FIG. 7, the two external gears 80 and 82 are formed while ensuring the ease of processing by forming the large diameter portions 84A and 86A only on one end side of the through holes 84 and 86. When incorporating, the constant diameter portions 84B and 86B (having a constant inner diameter) are made to face each other. Thereby, two external gears 80 and 82 symmetrical in the axial direction are provided as a set, and the thrust force generated between the internal gears 16 can be considerably canceled out.

  In the modification shown in FIG. 8, a plurality of large diameter portions 94A and 96A are intermittently formed (two in this modification). As described above, when the large diameter portions 94A and 96A are formed intermittently, the external gears 90 and 92 transmit power to the inner roller 38 over almost the entire axial direction of the through holes 94 and 96. It is possible to prevent stress from concentrating on only a part of the through holes 94 and 96 in the axial direction. For example, when the grease is applied to the large diameter portions 94A and 96A at the time of assembly, the large diameter portions 94A and 96A can be used as a grease reservoir.

  In the above-described embodiment or modification, the boundary portion between the constant diameter portion and the large diameter portion is configured to be stepped or intersecting two straight lines. For example, the constant diameter portion Of course, it is possible to connect the large diameter portions with a rounded curve, and this is preferable from the viewpoint of “preventing stress concentration”.

  Moreover, in the said embodiment, the example of a structure by which the inner roller was covered on the inner pin was shown. When the inner pin is covered with the inner roller, the load on the sliding surface is small (compared to the configuration in which the inner pin slides directly with the through hole), so that the constant diameter part with a constant inner diameter, that is, finish machining Therefore, the effect of the present invention can be obtained more remarkably. However, the present invention can also be applied to a reduction gear of a type in which the inner pin slides directly into the through hole, and a corresponding effect can be obtained if the large diameter portion is formed even a little.

  In the above-described embodiment, two external gears are incorporated. However, in the eccentric oscillating type speed reducer according to the present invention, the number of external gears is limited to two. It may be one sheet or three or more sheets. When three external gears are incorporated, the three external gears may have the same shape, or the shape of the through hole of the external gear may be different on both sides and the center. In the case of an eccentric oscillating type speed reducer having three external gears, the external gear at the center in the axial direction often has difficulty in ensuring good lubricity. You may make it small compared with a toothed gear, and may make it not apply this invention only to a center external gear. That is, the present invention is not necessarily applied equally (or symmetrically) to all external gears.

  Furthermore, in the above embodiment, an example is shown in which the internal gear is fixed and the pin-shaped member is inserted into the through hole of the external gear, and revolves in synchronization with the rotation of the external gear. The present invention is a so-called frame rotation type eccentric oscillating type in which a pin-like member synchronized with the rotation component of an external gear constrains the rotation of the external gear through a through hole, and the internal gear rotates as an output member. It can also be applied to deceleration.

  In addition, the manufacturing method of an external gear is not limited to the method of the said embodiment, As long as the internal diameter of a through-hole is finally non-uniform | heterogenous in an axial direction, you may manufacture by what kind of method.

DESCRIPTION OF SYMBOLS 12, 14 ... External gear 16 ... Internal gear 22, 24 ... Eccentric body 34, 36 ... Through-hole 34A, 36A ... Large diameter part 34B, 36B ... Constant diameter part 38 ... Inner roller 40 ... Inner pin

Claims (7)

An external gear, an internal gear that is inscribed while the external gear swings, and a through-hole provided in the external gear, are in contact with the inner periphery of the through-hole, In an eccentric rocking type speed reducer comprising a pin-like member synchronized with the rotation component,
An eccentric oscillation type speed reducer characterized in that the inner diameter of the through hole is not uniform in the axial direction. In claim 1,
An eccentric oscillating type speed reducer characterized in that large-diameter portions having an inner diameter larger than the axial center of the through-hole are formed at both axial ends of the through-hole. In claim 1 or 2,
The eccentric oscillating speed reducer, wherein the through hole has a constant diameter portion having a constant inner diameter, and the inner diameter linearly expands in the axial direction from the constant diameter portion. In any one of Claims 1-3,
An eccentric oscillating type speed reducer characterized in that the through hole has a constant diameter portion having a constant inner diameter, and the axial range of the portion having a larger inner diameter is wider than the axial range of the constant diameter portion. Machine. In any one of Claims 1-4,
The through hole has a constant diameter portion having a constant inner diameter, and a large diameter portion having a larger inner diameter than the constant diameter portion,
An eccentric oscillating speed reducer characterized in that the finishing process is different between the constant diameter part and the large diameter part. In any one of Claims 1-5,
Eccentric oscillation characterized in that the maximum surface pressure between the inner periphery of the through hole and the pin-shaped member is set to be larger than the maximum surface pressure between the internal gear and the external gear. Mold reducer. An external gear, an internal gear that is inscribed while the external gear swings, and a through-hole provided in the external gear, are in contact with the inner periphery of the through-hole, In the manufacturing method of the external gear of the eccentric oscillating speed reducer provided with a pin-like member synchronized with the rotation component,
Forming a through hole in the material of the external gear;
Expanding the inner diameter of a part of the raw hole in the axial direction to a larger diameter;
After the step of increasing the diameter of the part, a step of curing the material of the external gear;
And a step of performing a finishing process on a portion of the raw hole not having a large diameter after the hardening process. A method of manufacturing an external gear of an eccentric rocking type reduction gear.

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