KR20190095877A - Eccentrically swinging reducer device and Method for supplying lubricant - Google Patents

Abstract

Provided is an eccentrically swinging reducer device capable of easily manufacturing a component member, which comprises: an internal tooth gear (16) provided in a casing (22); an external tooth gear (14) engaged with the internal tooth gear (16); a first carrier (18) provided at one side direction in an axial direction of the external tooth gear (14); a second carrier (20) provided at the other side direction in an axial direction of the external tooth gear (14); a first main bearing (24) provided between the casing (22) and the first carrier (18); and a second bearing (26) provided between the casing (22) and the second carrier (20). Axial movement to one side direction in an axial direction of the external tooth gear (14) is restricted by a first member in one direction of an inner ring or an outer ring of the first main bearing (24). Axial movement to the other side direction in an axial direction of the external tooth gear (14) is restricted by a second member in one direction of an inner ring or an outer ring of the second main bearing (26). Moreover, a total value of an axial gap existing between the first member and the second member.

Description

Eccentrically swinging reducer device and method for supplying lubricant}

This application claims priority based on Japanese Patent Application No. 2018-019968, filed February 7, 2018. The entire contents of that application are incorporated herein by reference.

The present invention relates to an eccentric oscillation reduction device and a feeding method of a lubricant for the device.

The present applicant has disclosed an eccentric oscillation type reducer including an external gear that is oscillated by the eccentric body described in Patent Document 1 and an internal gear that the external gear is inscribed with and engaged with.

Patent Document 1: Japanese Unexamined Patent Publication No. 2013-124730

The deceleration device is replenished with lubricant such as grease from the outside as necessary in the engagement portion between the external gear and the internal gear. For this reason, it is preferable that the speed reduction apparatus is easy to supply a lubricant inside. The speed reducer of patent document 1 ensures an axial clearance between the main bearing which supports a carrier body, and an external gear, and forms the axial convex part which abuts against an external gear at a predetermined position of a carrier body. This responds to this problem. For such a deceleration device, it is required to facilitate the manufacture of the constituent members of the device including the carrier body.

SUMMARY OF THE INVENTION An object of the present invention has been made in view of such a problem, and an object of the present invention is to provide an eccentric oscillation type reduction device capable of facilitating manufacture of a constituent member.

MEANS TO SOLVE THE PROBLEM In order to solve the said subject, the eccentric oscillation type reduction apparatus of one aspect of this invention is the internal gear provided in the casing, the external gear which meshes with the internal gear, the 1st carrier provided in the axial one side of an external gear, And a second carrier provided on the other side in the axial direction of the outer gear, a first main bearing provided between the casing and the first carrier, and a second main bearing provided between the casing and the second carrier. The axial movement of the outer gear in the axial direction is regulated by a first member which is one of the inner ring or the outer ring of the first main bearing, and the axial movement of the outer gear in the axial direction of the second main bearing is It is regulated by the 2nd member which is one of an inner ring or an outer ring, and the total value of the axial clearance gap which exists between a 1st member and a 2nd member is 0.09 mm or more.

Another aspect of the invention is a method of feeding (or also referred to as "lubrication") of a lubricant. This method is a method of supplying a lubricant to the eccentric oscillation reduction apparatus described above, wherein the lubricant is supplied at a discharge pressure of 2.5 MPa or less from the apparatus for discharging the lubricant. Can be discharged).

However, any combination of the above components and those in which the components and expressions of the present invention are replaced with each other between methods and systems are also effective as aspects of the present invention.

According to the present invention, it is possible to provide an eccentric oscillation type reduction device capable of facilitating the production of a constituent member.

BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a side sectional view showing an eccentric oscillation type reduction device of the first embodiment.
FIG. 2 is an enlarged view illustrating the periphery of the first main bearing and the second main bearing of the eccentric oscillation reduction device of FIG. 1.
FIG. 3 is an explanatory view for explaining a lubricant feeding method for the eccentric swing reduction device of FIG. 1.
4 is a graph showing the relationship between the total value of the axial gaps between the main bearings and the paper feed amount.
Fig. 5 is a side sectional view showing the eccentric oscillation reduction device of the second embodiment.
Fig. 6 is a side sectional view showing the eccentric oscillation type reduction device of the third embodiment.

EMBODIMENT OF THE INVENTION Hereinafter, this invention is demonstrated, referring each figure based on suitable embodiment. In embodiment, a comparative example, and a modification, the same code | symbol is attached | subjected to the component which is the same or equivalent, and the description overlapping suitably is abbreviate | omitted. In addition, the dimension of the member in each figure is expanded and reduced suitably, in order to make understanding easy. In addition, in the drawings, some of the members which are not important in describing the embodiments are omitted.

In addition, terms including ordinal numbers such as first and second are used to describe various components, but the term is used only to distinguish one component from other components, and the term The component is not limited by the above.

[First Embodiment]

EMBODIMENT OF THE INVENTION Hereinafter, with reference to drawings, the structure of the eccentric oscillation reduction apparatus 10 which concerns on 1st Embodiment is demonstrated. 1 is a side sectional view showing an eccentric oscillation type reduction device 10 of the first embodiment. The eccentric oscillation type reduction apparatus 10 of this embodiment oscillates the external gear which meshes with an internal gear, produces | generates the rotation of one of the internal gear and the external gear, and drives the generated motion component from an output member. It is an eccentric oscillation gear device that outputs to

The eccentric oscillation type reduction device 10 mainly includes an input shaft 12, an external gear 14, an internal gear 16, a carrier 18, 20, a casing 22, and a main bearing 24. And a paper feed port 80. Hereinafter, the direction along the central axis La of the internal gear 16 is called "axial direction", and the circumferential direction and the radial direction of the circle centering on the central axis La are "circumferential direction" and "diameter, respectively" Direction ". In addition, hereafter, one side (right side in drawing) of an axial direction is called an input side for convenience, and the other side (left side in drawing) is called a half input side.

The input shaft 12 is rotated around the rotation center line by the rotational power input from a driving device (not shown). The eccentric oscillation type reduction apparatus 10 of this embodiment is a center crank type in which the rotation center line of the input shaft 12 is provided on the coaxial line with the center axis line La of the internal gear 16. The drive device is, for example, a motor, a gear motor, an engine, or the like.

The input shaft 12 of the present embodiment is a crank shaft having a plurality of eccentric portions 12a for swinging the outer gear 14. The axial center of the eccentric part 12a is eccentric with respect to the rotation center line of the input shaft 12. In the present embodiment, two eccentric portions 12a are provided, and the eccentric phases of the adjacent eccentric portions 12a are shifted by 180 degrees.

The outer gear 14 is provided individually corresponding to each of the some eccentric part 12a. The outer gear 14 is rotatably supported by the corresponding eccentric part 12a via the eccentric bearing 30. The outer gear 14 is formed with a pin hole 14a through which the pin member 32 penetrates. A gap is provided between the pin member 32 and the pin hole 14a as a margin for absorbing the rocking component of the external gear 14. The pin member 32 and the inner wall surface of the pin hole 14a contact in part.

The internal gear 16 meshes with the external gear 14. The internal gear 16 of this embodiment is rotatably supported by the inner peripheral part of the casing 22, and has the some outer pin 16a which comprises the internal tooth of the internal gear 16. As shown in FIG. The internal dimension of the internal gear 16 (the number of the outer pins 16a) is one more than the external dimension of the external gear 14 in this embodiment.

The casing 22 has a cylindrical shape as a whole, and an internal gear 16 is provided on the inner circumferential portion thereof. An annular flange portion 22a is provided on the outer circumferential portion of the casing 22. The flange part 22a is provided in the radially outer side with respect to the engagement position of the internal gear 16 and the external gear 14. The flange portion 22a is formed with a female screw hole 22b through which the screw member can be screwed in the circumferential direction.

The carriers 18, 20 are disposed on the axial side of the outer gear 14. The carriers 18 and 20 include a first carrier 18 disposed on the side of the input gear of the external gear 14 and a second carrier 20 disposed on the side of the half input side of the external gear 14. . The carriers 18 and 20 have a disk shape, and rotatably support the input shaft 12 through the input shaft bearing 34.

The first carrier 18 and the second carrier 20 are connected through the pin member 32. The pin member 32 penetrates the some external gear 14 in the axial direction at the position offset radially from the axial center of the external gear 14. Although the pin member 32 of this embodiment is provided integrally as a part of the same member as the 2nd carrier 20, you may provide separately from the carrier 18 and 20. FIG. The pin member 32 is provided in multiple numbers by the circumference | surroundings of the central axis La of the internal gear 16. As shown in FIG.

The pin member 32 of this embodiment is formed with the female screw hole 32a which opens to the cross section of an axial direction. The first carrier 18 is formed with an insertion hole 38 having a step in which the screw member 36 is inserted from the side opposite to the pin member 32 with the first carrier 18 therebetween. The pin member 32 is fixed to the first carrier 18 by turning the screw member 36 into the female screw hole 32a. However, in the first carrier 18 of the present embodiment, a pin hole 40 into which the tip end portion of the pin member 32 is fitted is formed.

A member for outputting rotational power to the driven device is an output member, and a member fixed to an external member for supporting the eccentric oscillation reduction device 10 is a fixed member. The output member of this embodiment is a casing 22, and the fixed member is a second carrier 20. The output member is rotatably supported by the fixed member via the main bearings 24 and 26.

2 is an enlarged view showing the main bearings 24 and 26 together with a part of the peripheral structure. The main bearings 24 and 26 are disposed between the first main bearing 24 disposed between the first carrier 18 and the casing 22, and the second carrier 20 and the casing 22. A second main bearing 26 is included. In the present embodiment, the pair of main bearings 24 and 26 are arranged in a state of so-called back combination.

The main bearings 24 and 26 of this embodiment are equipped with the some rolling element 42 and the retainer (not shown). The plurality of rolling elements 42 are provided to be interposed in the circumferential direction. The rolling element 42 of this embodiment is a sphere. The retainer rotatably supports the plurality of rolling elements 42 while maintaining the relative positions of the plurality of rolling elements 42.

Although the main bearings 24 and 26 of this embodiment are provided with the outer ring 48 in which the outer rolling surface which the rolling element 42 drives is provided, it has the inner ring in which the inner rolling surface which the rolling element 42 drives is provided. I never do that. Instead, the inner raceway surface is provided on the outer circumferential surface of the carriers 18 and 20. The outer raceway surface is provided on the radially outer side of the rolling element 42, and the inner raceway surface is provided on the radially inner side of the rolling element 42. The outer ring 48 is integrated with the casing 22 by fitting such as an interference fit or an intermediate fit.

Preload may be provided to the main bearings 24 and 26. The preload is mainly provided for securing bearing characteristics such as moment rigidity of the main bearings 24 and 26. In the present embodiment, the angular ball bearings are exemplified as the main bearings 24 and 26. In addition, the main bearings 24 and 26 may be rolling bearings, such as a taper roller bearing and an angular roller bearing mentioned later.

(Feed area)

Next, the paper feed port 80 will be described. In the eccentric oscillation type reduction device 10, it is preferable to replenish a lubricant such as grease in the engagement portion of the external gear 14 and the internal gear 16 and the inside thereof as necessary. For this reason, the eccentric oscillation type reduction apparatus 10 is provided with the paper feed port 80 which supplies a lubricant from the exterior. The paper feeding port 80 may be disposed anywhere as long as it can supply a lubricant to the inside of the eccentric oscillation reduction device 10. As shown in FIG. 2, the paper feed port 80 of this embodiment is provided in the flange part 22a, and is formed as a channel | path which penetrates radially from the outer peripheral surface of the flange part 22a to the inner peripheral surface of the casing 22. As shown in FIG. do. Although not shown, the eccentric oscillation reduction device 10 is also provided with a discharge port (or may be referred to as an "drain hole").

The supply path of the lubricant is preferably short. For this reason, the paper feed port 80 of this embodiment opens in the opposing surface 22h which opposes the outer gear 14 of the casing 22. Since the paper feed port 80 opens at a position facing the outer gear 14, the supply path of the lubricant can be shortened. Specifically, the paper feed port 80 is opened between the outer pin 16a and the outer pin 16a.

3 is an explanatory diagram for explaining a method of feeding a lubricant to the eccentric oscillation type reduction apparatus 10. For feeding the eccentric oscillation type reduction device 10, a discharge device 88 that pressurizes a lubricant and discharges it from the discharge port 88b is used. 3, the lubricant is discharged from the discharge device 88 at a predetermined discharge pressure as shown in FIG. When the discharge port 88b is connected to the paper feed port 80, in order to reduce the damage of the paper feed port 80, the discharge port 88b is formed of a material softer than the paper feed port 80 (for example, resin). It is desirable to be.

(Axial gap)

See FIG. 2. The outer gear 14 of the present embodiment is configured to be movable in the axial direction between the first main bearing 24 and the second main bearing 26. When the outer gear 14 moves excessively, the contact width of the outer gear 14 and the eccentric bearing 30 decreases, the surface pressure at the contact portion increases, and there is a fear of premature damage. For this reason, in this embodiment, the axial movement to the input side of the outer gear 14 is restrict | limited by the outer ring 48 of the 1st main bearing 24, and the outer ring 48 of the 2nd main bearing 26 is carried out. By this, the axial movement of the external gear 14 to the half input side is restricted. That is, the two outer gears 14 are movable in the axial direction between the outer ring 48 of the first main bearing 24 and the outer ring 48 of the second main bearing 26, and these members Several axial gaps are formed in the liver.

In the present embodiment, three gaps G1, G2, and G3 defined below are formed. The clearance in the axial direction between the outer ring 48 of the first main bearing 24 and the outer gear 14 on the input side is called a gap G1. The clearance in the axial direction between the external gear 14 on the input side and the external gear 14 on the half input side is called a gap G2. The clearance in the axial direction between the outer gear 14 on the half-input side and the outer ring 48 of the second main bearing 26 is called a gap G3. That is, between the outer ring 48 of the 1st main bearing 24 and the outer ring 48 of the 2nd main bearing 26, the axial clearance illustrated as a total value Gt of gaps G1, G2, G3. This exists. However, in a structure in which these gaps are provided with separate members such as washers, the total value Gt of the gaps is reduced by the thickness in the axial direction of the separate member.

When the lubricant is supplied, the lubricant supplied from the paper feed port 80 has a axial gap existing between the outer ring 48 of the first main bearing 24 and the outer ring 48 of the second main bearing 26. Penetrates inside. If these axial gaps are too small, the movement from the outer side of the outer gear 14 of the lubricant supplied from the paper feed port 80 to the radially inner side may be remarkably inhibited. In this case, paper feeding may take time, and workability is significantly reduced.

The inventors have made intensive studies from the viewpoint of facilitating the supply of lubricant, and have found the relationship described below between the total value Gt of the axial gap and the feeding amount Sg per unit time. 4 is a graph showing the relationship between the total value Gt of the axial gap between the main bearings 24 and 26 and the feeding amount Sg per unit time when grease is supplied at a discharge pressure of 2.0 MPa. In Fig. 4, the horizontal axis represents the total value Gt of the axial gap, and the vertical axis represents the paper feed amount Sg per unit time (1 minute). In FIG. 4, each point plots the paper feed amount Sg corresponding to the total value Gt.

As shown in Fig. 4, when the total value Gt of the axial gap is less than 0.09 mm, the feeding amount Sg per unit time is small, and the lubricant hardly penetrates inside. However, when the total value Gt of the axial gap is 0.09 mm or more, the feeding amount Sg per unit time becomes large, and the lubricant smoothly penetrates inside. That is, by setting the total value Gt of the axial gap existing between the outer ring 48 of the first main bearing 24 and the outer ring 48 of the second main bearing 26 to 0.09 mm or more, Supply becomes easy.

In FIG. 4, the case where the total value Gt of the axial gap exceeds 0.15 mm is not shown. However, even if the total value Gt exceeds 0.15 mm, the feed amount Sg per unit time increases so much. I never do that. On the other hand, if the total value Gt of the axial gap is too large, the margin in the axial direction of the external gear 14 may increase, resulting in a decrease in rotational accuracy. The inventors have repeatedly examined and confirmed that the problem caused by excessive gap is practically not impaired in the range where the total gap Gt satisfies the formula (1).

Equation (1): Gt≤0.13mm + 0.7 × Nmm

However, N is the number of axial gaps existing between the outer ring of the first main bearing 24 and the outer ring of the second main bearing 26. In this embodiment, the number of gaps is three of G1, G2, and G3, and N = 3. However, when separate members such as washers are interposed in these axial gaps, the number N of the axial gaps increases by the number of the separate members.

In particular, from the viewpoint of suppressing premature damage due to the reduction in contact width between the outer gear 14 and the eccentric bearing 30, the total value Gt of the axial gap is preferably 0.13 mm or less.

In order to shorten the working time of the lubricant supply, it is conceivable to increase the discharge pressure of the discharge device 88. In this case, it is conceivable that the discharge device 88 is enlarged to increase the power consumption. In addition, if the discharge pressure is excessively increased, the discharge port 88b expands, and a gap is generated between the discharge port 88b and the paper feed port 80, and there is a fear that the lubricant leaks from the gap. In view of this, the inventors have repeatedly studied the discharge pressure from the discharge device for discharging the lubricant when feeding the lubricant. As a result, it was confirmed that there is no problem in practical use when the lubricant is discharged to the paper feed port 80 at a discharge pressure of 2.5 MPa or less.

The operation of the eccentric oscillation reduction device 10 configured as described above will be described. When rotational power is transmitted from the drive device to the input shaft 12, the eccentric portion 12a of the input shaft 12 rotates around the rotation center line passing through the input shaft 12, and the external gear 12a is driven by the eccentric portion 12a. 14) swings. At this time, the outer gear 14 oscillates so that its shaft center rotates around the rotation center line of the input shaft 12. When the outer gear 14 swings, the engagement positions of the outer gear 14 and the inner gear 16 are sequentially shifted. As a result, whenever the input shaft 12 rotates once, the rotation of one of the external gear 14 and the internal gear 16 occurs by the correspondence of the dimension difference between the external gear 14 and the internal gear 16. do. In this embodiment, the internal gear 16 rotates and the deceleration rotation is output from the casing 22.

[Second embodiment]

Next, the structure of the eccentric oscillation reduction apparatus 10 which concerns on 2nd Embodiment is demonstrated. In the drawings and the description of the second embodiment, the same or equivalent components and members as those in the first embodiment are denoted by the same reference numerals. Description overlapping with 1st Embodiment is abbreviate | omitted suitably, and the structure different from 1st Embodiment is demonstrated mainly. FIG. 5 is a side sectional view showing the eccentric oscillation reduction device 10 of the second embodiment, and corresponds to FIG. 1. While the first embodiment includes two outer gears 14 and two eccentric portions 12a, the eccentric oscillation type reduction device 10 of the second embodiment includes three outer gears 14 and three. It differs in the point which has two eccentric parts 12a, and the other structure is the same. In the second embodiment, three eccentric portions 12a are provided, and the eccentric phases of the respective eccentric portions 12a are shifted by 120 degrees.

As shown in FIG. 5, in this embodiment, three outer teeth are provided between the outer ring 48 of the first main bearing 24 and the outer ring 48 of the second main bearing 26 in the axial direction. Gear 14 is present, and four gaps G1, G2, G3, G4 can be formed between these members. A gap G1, G2, G3, G4 exists between the outer ring 48 of the 1st main bearing 24 and the outer ring 48 of the 2nd main bearing 26, and the total value Gt of these axial clearances is present. Is 0.09mm or more and is set to 0.13mm or less. Moreover, this embodiment has the paper feed opening 80 which opens to the surface which faces the outer gear 14 of the casing 22.

The eccentric oscillation reduction apparatus 10 according to the second embodiment configured as described above operates in the same manner as the eccentric oscillation reduction apparatus 10.

[Third embodiment]

Next, the structure of the eccentric oscillation reduction apparatus 10 which concerns on 3rd Embodiment is demonstrated. In the drawings and description of the third embodiment, the same or equivalent components and members as those of the first embodiment are denoted by the same reference numerals. Description overlapping with 1st Embodiment is abbreviate | omitted suitably, and the structure different from 1st Embodiment is demonstrated mainly. FIG. 6 is a side sectional view showing the eccentric oscillation type reduction device 10 of the third embodiment, and corresponds to FIG. 1.

The first embodiment has described the center crank type eccentric oscillation gear device as an example. The eccentric oscillation type reduction gear of the present embodiment is a so-called split type eccentric oscillation gear device. In comparison with the first embodiment, the eccentric oscillation type reduction device 10 of the present embodiment mainly includes a plurality of input gears 70, or points of the input shaft 12 and the main bearings 24, 26. Is different from.

The plurality of input gears 70 are arranged around the central axis La of the internal gear 16. In this figure, only one input gear 70 is shown. The input gear 70 is supported by the input shaft 12 inserted into the center portion thereof, and is provided to be integrally rotatable with the input shaft 12. The input gear 70 meshes with an outer tooth portion of a rotating shaft (not shown) provided on the central axis La of the internal gear 16. The rotational power is transmitted from the driving device (not shown) to the rotating shaft, and the input gear 70 rotates integrally with the input shaft 12 by the rotation of the rotating shaft.

The input shaft 12 of this embodiment is arrange | positioned in multiple numbers (for example, three) at intervals in the circumferential direction at the position offset from the center axis line La of the internal gear 16. In this figure, only one input shaft 12 is shown.

The main bearings 24 and 26 of this embodiment are tapered roller bearings, ie, rolling bearings. The rolling element 42 of this embodiment is a conical roller. In the case where the main bearings 24 and 26 are rolling bearings as in the present embodiment, the main bearings 24 and 26 usually have an inner ring 72 provided with an inner raceway in addition to the outer race 48 provided with the outer raceway. Equipped.

As shown in FIG. 6, in this embodiment, two outer teeth are provided between the outer ring 48 of the first main bearing 24 and the outer ring 48 of the second main bearing 26 in the axial direction. The gear 14 exists, and three gaps G1, G2, G3 can be formed between these members. Between the outer ring 48 of the 1st main bearing 24 and the outer ring 48 of the 2nd main bearing 26, clearance gaps G1, G2, G3 exist, and the total value Gt of these axial clearances is 0.09. mm or more and 0.13 mm or less. Moreover, this embodiment has the paper feed opening 80 which opens to the surface which faces the outer gear 14 of the casing 22.

The operation of the eccentric oscillation type reduction device 10 of the present embodiment is described above. When the rotational power is transmitted from the drive device to the rotational shaft, the rotational power is divided from the rotational shaft to the plurality of input gears 70, and each input gear 70 rotates in the same phase. As each input gear 70 rotates, the eccentric portion 12a of the input shaft 12 rotates around the rotation center line passing through the input shaft 12, and the outer gear 14 swings by the eccentric portion 12a. do. When the outer gear 14 swings, similarly to the first embodiment, the engagement positions of the outer gear 14 and the inner gear 16 are sequentially shifted, and the outer gear 14 and the inner gear 16 of one side are shifted. Rotation occurs. The rotation of the input shaft 12 is decelerated at a reduction ratio corresponding to the size difference between the external gear 14 and the internal gear 16, and is output from the output member to the driven device.

The outline | summary of one aspect of this invention is as follows. The eccentric oscillation type reduction apparatus 10 of 1 aspect of this invention is the internal gear 16 provided in the casing 22, the external gear 14 meshed with the internal gear 16, and the external gear 14 of the internal gear. The first carrier 18 provided on one side of the axial direction, the second carrier 20 provided on the other side of the outer gear 14 in the axial direction, and the first provided between the casing 22 and the first carrier 18. The 1st main bearing 24 and the 2nd main bearing 26 provided between the casing 22 and the 2nd carrier 20 are provided. The axial movement of the outer gear 14 in the axial direction is regulated by a first member which is one of the inner ring or the outer ring of the first main bearing 24, and the shaft of the outer gear 14 in the axial direction is opposite. Directional movement is regulated by a second member which is one of the inner ring or outer ring of the second main bearing 26, and the total value Gt of the axial gap existing between the first member and the second member is 0.09 mm. That's it.

According to this aspect, while the axial movement of the external gear 14 is regulated by the first and second main bearings, the lubricant smoothly penetrates into the interior as compared with the case where the total value Gt of the axial gap is too small. , Supply of lubricant becomes easy. Therefore, the shape of a carrier can be simplified, and the manufacture of a carrier becomes easy, without having to provide a control part of an external gear in a carrier.

When the number of axial gaps existing between the first member and the second member is N, the total value Gt of the axial gaps satisfies the formula (1): Gt ≦ 0.13mm + 0.7 × Nmm. do. In this case, as compared with the case where the total value Gt of the axial gap is too large, the margin of the outer gear 14 in the axial direction can be reduced to suppress the decrease in rotational precision.

The total value Gt of the axial gap may be 0.13 mm or less. In this case, the margin of the outer gear 14 in the axial direction can be further reduced to further suppress the decrease in rotational precision.

You may have the paper feed port 80 opening in the surface which faces the external gear 14 of the casing 22. As shown in FIG. In this case, the path from the paper feed port 80 to the external gear 14 can be shortened, and the lubricant can be supplied more smoothly.

Another aspect of the present invention is a method of feeding a lubricant. This method is a method of supplying a lubricant to the eccentric oscillation type reduction device 10, and includes discharging the lubricant to the paper feed port 80 at a discharge pressure of 2.5 MPa or less from the discharge device 88 for discharging the lubricant. have. According to this aspect, the discharge device 88 can be downsized and power consumption can be suppressed as compared with the case where the discharge pressure is large. In addition, the seal structure of the lubricant in the paper feed path from the discharge device 88 to the paper feed port 80 can be simplified.

In the above, the example of embodiment of this invention was described in detail. All the above-mentioned embodiments show only the specific example in implementing this invention. The contents of the embodiments do not limit the technical scope of the present invention, and many design changes such as change, addition, and deletion of components can be made without departing from the spirit of the invention defined in the claims. In the above-described embodiment, descriptions such as "in embodiments" and "in embodiments" described with reference to the contents that can be changed in such a design, but the design change is not allowed in the content without such a notation. no. In addition, hatching displayed in the cross section of a figure does not limit the material of the object which displayed the hatching.

Modifications will be described below. In the drawings and the description of the modifications, the same or equivalent components and members as those of the embodiment are given the same reference numerals. Description overlapping with the embodiment will be omitted as appropriate, and the configuration different from the first embodiment will be mainly described.

In 1st Embodiment, although the 1st main bearing 24 and the 2nd main bearing 26 demonstrated the example which does not have an inner ring, this invention is not limited to this. At least one of the 1st main bearing 24 and the 2nd main bearing 26 may be a bearing which has an inner ring.

In the first embodiment, an example in which axial movement of the outer gear 14 is restricted by the outer ring 48 of each of the first main bearing 24 and the second main bearing 26 has been described. It is not limited. The axial movement of the outer gear 14 may be restricted by the inner ring of the main bearing. In this case, the total value Gt of the axial gap existing between the inner ring of the first main bearing 24 and the inner ring of the second main bearing 26 is set to 0.09 mm or more.

The output member of embodiment is the casing 22, and the example which fixed the carrier 18 and 20 to the outer member was demonstrated. In addition, the output members are the carriers 18 and 20, and the casing 22 may be fixed to the outer member.

Although the example which provided the opening of the paper feed port 80 in the outer peripheral surface of the flange part 22a of the casing 22 was demonstrated, the paper feed port 80 is provided in the position which avoided the flange part 22a of the casing 22. You may also In addition, the paper feed port 80 may be provided in parts other than a casing, for example, a carrier.

Each modification mentioned above shows the same effect and effect as 1st Embodiment.

Any combination of the above-described embodiments and modifications is also useful as an embodiment of the present invention. The new embodiment generated by the combination combines the effects of each of the embodiments and the modified examples to be combined.

10... Eccentric Oscillation Reduction Gear
12... Input shaft
14... Shout
16... Mine
18... First carrier
20... Second carrier
22... Casing
24... Primary bearing
26... 2nd main bearing
30... Eccentric Bearing
32... Pin member
34... Input shaft bearing
36.. Screw member
38... Insertion hole
40... Pinhole
42... Rolling element
48... paddle
70... Input gear
72... Inner ring
80... Paper feeder
88... Discharge device

Claims (5)

The internal gear in the casing,
The external gear that meshes with the above
A first carrier provided on one side of the outer gear in the axial direction;
A second carrier provided on the other side in the axial direction of the external gear,
A first main bearing provided between the casing and the first carrier,
A second main bearing provided between the casing and the second carrier,
The axial movement of the outer gear toward the axial one side is regulated by a first member which is one of the inner ring or the outer ring of the first main bearing,
The axial movement of the outer gear to the other side in the axial direction is regulated by a second member which is one of the inner ring or the outer ring of the second main bearing,
The total value of the axial gap existing between the first member and the second member is 0.09 mm or more. The method of claim 1,
When the number of axial gaps existing between the first member and the second member is N, the total value of the axial gaps is,
Equation (1): Eccentric oscillation type reduction gear, characterized in that the total value of the axial gaps ≤ 0.13 mm + 0.7 x Nmm. The method according to claim 1 or 2,
Eccentric oscillation type reduction device, characterized in that the total value of the axial gap is 0.13mm or less. The method according to claim 1 or 2,
An eccentric oscillation reduction device, characterized in that it has a paper feed opening that opens on a surface of the casing facing the outer gear. A method for supplying a lubricant to an eccentric oscillation type reduction device according to claim 4, comprising: discharging the lubricant to the feed port at a discharge pressure of 2.5 MPa or less from a discharge device for discharging the lubricant. How to feed

Images