JP2021067308A - Series of gear devices, and manufacturing method and design method therefor - Google Patents

Abstract

To provide gear devices having desired performance at low cost.SOLUTION: A series of gear devices includes a first gear device (10) and a second gear device (20). Each of the first gear device (10) and the second gear device (20) is a deflection engagement type gear device comprising an internal gear, an external gear, a vibrating body for deflecting and deforming the external gear, and a vibrating body bearing arranged between the external bearing and the vibrating body. In the first gear device (10) and the second gear device (20), at least the shape of the internal gears the same as each other. An interference (δ1) between the external gear (11) and an outer ring (12a) of the vibrating body bearing (12) in the first gear device (10) is different from an interference (δ2) between the external gear (21) and an outer ring (22a) of the vibrating body bearing (22) in the second gear device (20).SELECTED DRAWING: Figure 3

Description

The present invention relates to a series of gear devices, a manufacturing method and a design method thereof.

Conventionally, a flexural meshing gear device including an external tooth gear that flexes and deforms is known (see, for example, Patent Document 1). The external tooth gear is internally fitted with a oscillating body via a oscillating body bearing, and the oscillating body rotates inward to bend and deform. In addition, the external gear meshes with the rigid internal gear.

The performance of this type of gear device is the spring constant, which represents the torsional rigidity of the power transmission system. In order to improve this spring constant, it is necessary to take measures such as increasing the number of meshes of the gears and increasing the rim thickness (thickness between the tooth bottom and the inner circumference) of the external gear. However, these measures increase the power loss and reduce the power transmission efficiency.
Therefore, in order to adjust the spring constant and power transmission efficiency, which are in a trade-off relationship, and to obtain these performances as desired, it is necessary to make major component changes such as changing the tooth profile even at the same reduction ratio. It was necessary, which led to a rise in product costs.

Japanese Unexamined Patent Publication No. 2014-199130

The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a gear device having desired performance at low cost.

The series of gear devices according to the present invention is
A series of gear devices including a first gear device and a second gear device.
Each of the first gear device and the second gear device is between an internal gear, an external gear, a oscillating body that bends and deforms the external gear, and the external gear and the oscillating body. It is a flexible meshing type gear device having a oscillating body bearing arranged in.
In the first gear device and the second gear device, at least the internal gears have the same shape, and the tightening margins between the external gears and the outer ring of the oscillating body bearing are different from each other.

The method for manufacturing the gear device group according to the present invention is as follows.
A method for manufacturing a group of gear devices including a first gear device and a second gear device.
Each of the first gear device and the second gear device is between an internal gear, an external gear, a oscillating body that bends and deforms the external gear, and the external gear and the oscillating body. It is a flexible meshing type gear device having a oscillating body bearing arranged in.
In the first gear device and the second gear device, at least the internal gears have the same shape as each other.
A manufacturing process of the first gear device including a step of fitting the external gear of the first gear device and the outer ring of the exciting body bearing with a first tightening allowance, and a manufacturing process of the first gear device.
A manufacturing process of the second gear device including a step of fitting the external gear of the second gear device and the outer ring of the oscillating body bearing with a second tightening allowance different from the first tightening allowance. , Was provided.

The method for designing the gear device group according to the present invention is as follows.
It is a design method of a gear device group including a first gear device and a second gear device.
Each of the first gear device and the second gear device is between an internal gear, an external gear, a oscillating body that bends and deforms the external gear, and the external gear and the oscillating body. It is a flexible meshing type gear device having a oscillating body bearing arranged in.
In the first gear device and the second gear device, at least the internal gears have the same shape as each other.
The distance between the external gear of the first gear device and the outer ring of the exciting body bearing is set as the first tightening allowance.
The external gear of the second gear device and the outer ring of the oscillating body bearing are set to a second tightening allowance different from the first tightening allowance.

According to the present invention, a gear device having desired performance can be provided at low cost.

It is sectional drawing which shows the 1st gear device which concerns on this Embodiment. It is a figure for demonstrating the spring constant. It is sectional drawing which shows the 2nd gear device which concerns on this Embodiment. It is a figure for demonstrating the tightening allowance between an external gear and an outer ring of a oscillating body bearing, (a) is a figure which shows the tightening allowance of a 1st gear device, and (b) is a figure which shows the tightening allowance of a 2nd gear device. It is a figure which shows the tightening allowance.

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

The series of gear devices according to the present embodiment is a product group of flexible meshing type gear devices including the first gear device 10 and the second gear device 20.

[Configuration of first gear device]
First, the configuration of the first gear device 10 according to the present embodiment will be described. FIG. 1 is a cross-sectional view showing the first gear device 10.
As shown in this figure, the first gear device 10 includes the exciter shaft 30, the external gear 11, the first internal gear 31G and the second internal gear 32G, the exciter bearing 12, the casing 33, and the first. A cover 34 and a second cover 35 are provided.

The exciter shaft 30 is a hollow tubular shaft that rotates around a rotation shaft O1, and has a non-circular (for example, elliptical) outer shape of a cross section perpendicular to the rotation shaft O1 and a vibrating body 30A. It has shaft portions 30B and 30C provided on both sides in the axial direction of 30A. The ellipse is not limited to a geometrically exact ellipse, but includes a substantially ellipse. The shaft portions 30B and 30C are shafts having a circular outer shape in a cross section perpendicular to the rotation shaft O1. The exciter shaft 30 is an input shaft connected to a drive source (not shown) such as a motor and to which a driving force is input.
In the following description, the direction along the rotation axis O1 is referred to as "axial direction", the direction perpendicular to the rotation axis O1 is referred to as "diametrical direction", and the rotation direction centered on the rotation axis O1 is referred to as "circumferential direction". Further, in the axial direction, the side that outputs the decelerated motion connected to the external mating member to the mating member (left side in the figure) is called the "output side", and the side opposite to the output side (in the figure). The right side of) is called the "anti-output side". Further, the inner diameter, outer diameter and PCD of each component of the exciter bearing and the external gear mean the inner diameter, outer diameter and PCD in the (round) state before being fitted to the exciter.

The external gear 11 is a cylindrical member having flexibility and centered on the rotating shaft O1, and is provided with teeth on the outer periphery.

The first internal gear 31G and the second internal gear 32G rotate around the rotating shaft 30 around the rotating shaft O1. The first internal gear 31G and the second internal gear 32G are provided side by side in the axial direction and mesh with the external gear 11. Specifically, one of the first internal gear 31G and the second internal gear 32G meshes with the tooth portion on one side of the center of the external gear 11 in the axial direction, and the other meshes with the tooth portion on one side from the center in the axial direction of the external gear 11. It meshes with the tooth on the other side of the center.
Of these, the first internal gear 31G is configured by providing internal teeth at the corresponding portion of the inner peripheral portion of the first internal gear member 31. On the other hand, the second internal gear 32G is configured by providing internal teeth at a corresponding portion of the inner peripheral portion of the second internal gear member 32.

The oscillating body bearing 12 is, for example, a roller bearing, and is arranged between the oscillating body 30A and the external gear 11. The exciter 30A and the external gear 11 can rotate relative to each other via the exciter bearing 12.
The oscillating body bearing 12 includes an outer ring 12a fitted inside the external gear 11 with a predetermined tightening allowance δ1, a plurality of rolling elements (rollers) 12b, and a cage 12c for holding the plurality of rolling elements 12b. Have.
The tightening allowance δ1 between the external gear 11 and the outer ring 12a is given by δ1 = (d12o−d11) / 2 from the inner diameter d11 of the external gear 11 and the outer diameter d12o of the outer ring 12a (FIG. 4 (a)). )reference). In the present embodiment, the tightening allowance δ1 is a positive value (δ1> 0), and the external gear 11 and the outer ring 12a of the oscillating body bearing 12 are press-fitted (tightened). However, the "tightening allowance" according to the present invention includes a value of zero or less (that is, when the external tooth gear and the outer ring of the oscillating body bearing are intermediate-fitted or gap-fitted).
The plurality of rolling elements 12b are arranged in the radial direction of the first internal gear 31G, and are arranged in the radial direction of the first group of rolling elements 12b arranged in the circumferential direction and the second internal gear 32G. It has a second group of rolling elements 12b arranged in the circumferential direction. These rolling elements 12b roll with the outer peripheral surface of the oscillator 30A and the inner peripheral surface of the outer ring 12a as rolling surfaces. Two outer rings 12a having the same shape are provided side by side in the axial direction corresponding to the arrangement of the plurality of rolling elements 12b. The oscillating body bearing 12 may have an inner ring that is separate from the oscillating body 30A.

Spacer rings 41 and 42 are provided on both sides of the oscillating body bearing 12 and the external gear 11 in the axial direction as regulating members that abut against them and regulate their movement in the axial direction.

The casing 33 covers the outer diameter side of the second internal gear 32G. The casing 33 is connected to the first internal gear member 31 via a connecting member such as a bolt. The casing 33 has an outer ring portion of the main bearing 38 formed on the inner peripheral portion, and rotatably supports the second internal gear member 32 via the main bearing 38.

The first cover 34 is connected to the first internal gear member 31 and covers the meshing portion between the external gear 11 and the first internal gear 31G from the counter-output side in the axial direction.
A bearing 36 is arranged between the first cover 34 and the shaft portion 30B of the exciter shaft 30, and the first cover 34 rotatably supports the exciter shaft 30 via the bearing 36. There is.

The second cover 35 is connected to the second internal gear member 32 and covers the meshing portion between the external gear 11 and the second internal gear 32G from the output side in the axial direction. The second cover 35 and the second internal gear member 32 are connected to an external mating member that outputs the decelerated motion.
A bearing 37 is arranged between the second cover 35 and the shaft portion 30C of the exciter shaft 30, and the second cover 35 rotatably supports the exciter shaft 30 via the bearing 37. There is.

Further, the first gear device 10 includes oil seals 43, 44, 45 for sealing and O-rings 46, 47, 48.
The oil seal 43 is arranged between the shaft portion 30B of the exciter shaft 30 and the first cover 34 at the end portion on the counter-output side in the axial direction, and suppresses the outflow of the lubricant to the counter-output side. The oil seal 44 is arranged at the end on the output side in the axial direction between the shaft portion 30C of the exciter shaft 30 and the second cover 35, and suppresses the outflow of the lubricant to the output side. The oil seal 45 is arranged between the casing 33 and the second internal gear member 32, and suppresses the outflow of the lubricant from this portion.
The O-rings 46, 47, 48 are provided between the first internal gear member 31 and the first cover 34, between the first internal gear member 31 and the casing 33, and between the second internal gear member 32 and the second cover. It is provided between the 35 and 35 to prevent the lubricant from moving between them.
That is, the lubricant is sealed in the seal space S inside the first gear device 10 sealed by the oil seals 43 to 45 and the O-rings 46 to 48. The lubricant used is not particularly limited and may be oil or grease.

[Deceleration operation of the first gear device]
Subsequently, the deceleration operation of the first gear device 10 will be described.
When the exciter shaft 30 is rotationally driven by a drive source such as a motor, the motion of the exciter 30A is transmitted to the external gear 11. At this time, the external gear 11 is restricted to a shape along the outer peripheral surface of the exciter 30A, and is bent into an elliptical shape having a long axis portion and a short axis portion when viewed from the axial direction. Further, the external gear 11 meshes with the fixed first internal gear 31G at a long shaft portion. Therefore, the external gear 11 does not rotate at the same rotation speed as the exciting body 30A, and the exciting body 30A rotates relatively inside the external gear 11. Then, with this relative rotation, the external gear 11 bends and deforms so that the major axis position and the minor axis position move in the circumferential direction. The period of this deformation is proportional to the rotation period of the exciter shaft 30.

When the external gear 11 bends and deforms, its long axis position moves, so that the meshing position between the external gear 11 and the first internal gear 31G changes in the rotational direction. Here, for example, assuming that the number of teeth of the external gear 11 is 100 and the number of teeth of the first internal gear 31G is 102, the external gear 11 and the first internal gear 31G are engaged every time the meshing position goes around. The meshing teeth of the teeth are displaced, which causes the external gear 11 to rotate (rotate). With the above number of teeth, the rotational motion of the exciter shaft 30 is decelerated at a reduction ratio of 100: 2 and transmitted to the external gear 11.

On the other hand, since the external gear 11 also meshes with the second internal gear 32G, the meshing position between the external gear 11 and the second internal gear 32G also changes in the rotation direction due to the rotation of the exciter shaft 30. .. Here, assuming that the number of teeth of the second internal gear 32G and the number of teeth of the external gear 11 are the same, the external gear 11 and the second internal gear 32G do not rotate relatively, and the external teeth The rotational movement of the gear 11 is transmitted to the second internal tooth gear 32G at a reduction ratio of 1: 1. As a result, the rotational movement of the exciter shaft 30 is decelerated at a reduction ratio of 100: 2 and transmitted to the second internal gear member 32 and the second cover 35, and this rotational movement is output to the mating member.

Here, in the first gear device 10, the tightening allowance δ1 is a positive value (δ1> 0), and the external gear 11 and the outer ring 12a of the oscillating body bearing 12 are press-fitted. Therefore, the rigidity between the external gear 11 and the outer ring 12a of the oscillating body bearing 12 is high, and the spring constant is large.
The spring constant is a performance parameter that represents the torsional rigidity of the power transmission system of the gear device (reduction device). FIG. 2 is a diagram for explaining the spring constant. Fix the input shaft (high-speed shaft) of the speed reducer, slowly apply a load from the output shaft (low-speed shaft) side to the rated torque, measure the load until unloading, and measure the displacement (twist angle) of the low-speed shaft, and the relationship. Then, a hysteresis curve having a rigidity as shown in FIG. 2 can be obtained. The spring constant is defined as the ratio of the torque difference to the torsion angle difference from a certain point (50% in the example of the figure) to 100% of the rated torque. In the first and second gear devices 10 and 20 of the present embodiment, the input shaft corresponds to the exciter shaft 30, and the output shaft corresponds to the second cover 35 and the second internal gear member 32.

On the other hand, since the external gear 11 and the outer ring 12a of the oscillating body bearing 12 are press-fitted, the external gear 11 and the outer ring 12a are more likely to shift in the circumferential direction during operation than when the tightening allowance δ1 is smaller. If the fitting portion is out of lubricating oil when the external gear 11 and the outer ring 12a are displaced, fretting is likely to occur. Therefore, it is necessary to enclose a sufficient amount of lubricant in the seal space S so that fretting does not occur. As a result, the stirring loss of the lubricating oil during operation becomes relatively large as compared with the case where the tightening margin δ1 is smaller, and the power transmission efficiency is lowered.

[Configuration of second gear device]
Subsequently, the configuration of the second gear device 20 according to the present embodiment will be described. FIG. 3 is a cross-sectional view showing the second gear device 20.
As shown in this figure, the second gear device 20 includes an external gear 21 and a oscillating body bearing 22. In the second gear device 20, the tightening allowance between the external gear 21 and the outer ring 22a of the oscillating body bearing 22 is different from that of the first gear device 10, and components not related to this tightening allowance (specifically, the outer ring). The tooth gear 21, the exciter bearing 22, and the exciter 30A) have the same configuration as that of the first gear device 10 (the shape and dimensions are the same). Here, "common (same shape and dimensions)" means that the shapes and dimensions are designed to be the same, and there are slight differences due to manufacturing errors and the like. Hereinafter, the differences from the first gear device 10 will be mainly described, and the components common to the first gear device 10 will be designated by the same reference numerals and detailed description thereof will be omitted.

The external gear 21 has the same shape as the external gear 11 of the first gear device 10.
That is, the external gear 21 is a cylindrical member having flexibility and centered on the rotating shaft O1, and is provided with teeth on the outer periphery.

The oscillating body bearing 22 has the same structure as the oscillating body bearing 12 of the first gear device 10.
That is, the oscillating body bearing 22 is, for example, a roller bearing, and is arranged between the oscillating body 30A and the external gear 21. The exciter 30A and the external gear 21 can rotate relative to each other via the exciter bearing 22.
The exciter bearing 22 includes an outer ring 22a fitted inside the external gear 21 with a tightening allowance δ2, a plurality of rolling elements (rollers) 22b, and a cage 22c for holding the plurality of rolling elements 22b. Have. The plurality of rolling elements 22b are arranged in the radial direction of the first internal gear 31G, and are arranged in the radial direction of the first group of rolling elements 22b arranged in the circumferential direction and the second internal gear 32G. It has a second group of rolling elements 22b arranged in the circumferential direction. These rolling elements 22b roll with the outer peripheral surface of the oscillator 30A and the inner peripheral surface of the outer ring 22a as rolling surfaces. Two outer rings 22a having the same shape are provided side by side in the axial direction corresponding to the arrangement of the plurality of rolling elements 22b. The oscillating body bearing 22 may have an inner ring that is separate from the oscillating body 30A.

In these external gears 21 and the exciter bearing 22, the tightening allowance δ2 between the external gear 21 and the outer ring 22a of the exciter bearing 22 is different from the tightening allowance δ1 of the first gear device 10.
4A and 4B are views for explaining a tightening allowance between the external gear and the outer ring of the exciter bearing, in which FIG. 4A shows a tightening allowance δ1 of the first gear device 10, FIG. 4B. Is a diagram showing a tightening allowance δ2 of the second gear device 20. In FIG. 4, the tightening margins δ1 and δ2 are enlarged more than they actually are for the sake of clarity.
As shown in these figures, the tightening allowance δ2 is given by δ2 = (d22o−d21) / 2 from the inner diameter d21 of the external gear 21 and the outer diameter d22o of the outer ring 22a. The tightening allowance δ2 of the present embodiment is smaller than the tightening allowance δ1 of the first gear device 10 and has a negative value. That is, the external gear 21 and the outer ring 22a of the oscillating body bearing 22 are fitted in a gap.

In the present embodiment, the inner diameter d21 of the external gear 21 is the same as the inner diameter d11 of the external gear 11 in the first gear device 10, and the outer diameter d22o of the outer ring 22a of the exciter bearing 22 is the first gear device 10. It is different from the outer diameter d12o of the outer ring 12a of the exciter bearing 12 in the above. Specifically, the outer diameter d22o of the outer ring 22a is smaller than the outer diameter d12o of the outer ring 12a in the first gear device 10. As a result, the tightening allowance δ2 of the second gear device 20 is smaller than the tightening allowance δ1 of the first gear device 10.
Further, as described above, the fitting portion between the outer diameter d22o of the outer ring 22a and the inner diameter d21 of the outer gear 21 may be displaced from each other during operation, resulting in fretting. Therefore, in the case of gap fitting with a small tightening margin, the outer diameter d22o of the outer ring 22a has a predetermined radius of curvature relationship (gap relationship) so that the outer diameter d22o of the outer ring 22a is less likely to be displaced from the inner diameter d21 of the outer gear 21. It is preferable to form. As a result, the occurrence of fretting in the fitting portion can be suppressed.

When the outer diameter d22o of the outer ring 22a is different from that of the first gear device 10, the thickness t22 of the outer ring 22a is the same as the thickness t12 of the outer ring 12a in the first gear device 10 from the viewpoint of the stress acting on the outer ring 22a during operation. Is preferable. That is, the inner diameter d22i of the outer ring 22a is made different from the inner diameter d12i of the outer ring 12a in the first gear device 10 by the same amount of change of the outer diameter d22o of the outer ring 22a with respect to the outer diameter d12o of the outer ring 12a in the first gear device 10. ) Is preferable. Since stress increases as the thickness of the outer ring increases, it is better to avoid making the outer ring thicker, but if there is room to reduce the thickness of the outer ring in terms of processing and simple strength, etc. The thickness of the tobacco may be reduced.

Even when the inner diameter d22i of the outer ring 22a is different from that of the first gear device 10, the rolling element 22b of the exciter bearing 22 can have the same shape as the rolling element 12b in the first gear device 10. ..
However, the pitch circle diameter PCD2 of the exciter bearing 22 is different from the pitch circle diameter PCD1 of the exciter bearing 12 in the first gear device 10. Therefore, in accordance with this, it is necessary to use a cage 22c of the oscillating body bearing 22 having an outer diameter and an inner diameter different (smaller) from the cage 12c of the oscillating body bearing 12 of the first gear device 10. is there. Further, the outer peripheral length of the oscillating body 30A of the second gear device 20, which is the inner ring of the oscillating body bearing 22, is different (smaller) from that of the oscillating body 30A of the first gear device 10 in accordance with the change in the pitch circle diameter. ) Need to be something.

In the external gear 21 and the exciter bearing 22, if the tightening allowance δ2 between the external gear 21 and the outer ring 22a of the exciter bearing 22 is different from the tightening allowance δ1 of the first gear device 10. Good. Therefore, if the outer diameter d22o of the outer ring 22a of the exciter bearing 22 remains the same as that of the first gear device 10, the inner diameter d21 of the outer gear 21 is different from the inner diameter d11 of the outer gear 11 in the first gear device 10. You may let me. However, as the rim thickness (thickness between the tooth bottom and the inner circumference) of the external gear increases, the stress acting on the external gear increases. Therefore, when reducing the inner diameter of the external gear, it is preferable to keep it within a range where there is no problem in terms of strength.
Further, both the outer diameter d22o of the outer ring 22a of the exciter bearing 22 and the inner diameter d21 of the outer gear 21 may be different from those of the first gear device 10. However, it goes without saying that the tightening allowance δ2 needs to be different from the tightening allowance δ1 of the first gear device 10.

[Deceleration operation of the second gear device]
Subsequently, the deceleration operation of the second gear device 20 will be described.
The second gear device 20 operates in the same manner as the first gear device 10. That is, when the exciting body shaft 30 is rotationally driven by a driving source such as a motor, the external gear 21 is bent and deformed by the exciting body 30A. Then, the external gear 21 rotates with respect to the first internal gear 31G according to the difference in the number of teeth between the first internal gear 31G and the second internal gear 32G, while the second internal gear 32G is Does not rotate relatively. As a result, the rotational movement of the exciter shaft 30 is decelerated, transmitted to the second internal gear member 32 and the second cover 35, and output to the mating member.

Here, in the second gear device 20, the tightening allowance δ2 is a negative value (δ1 <0) smaller than the tightening allowance δ1 of the first gear device 10, and the external gear 21 and the outer ring 22a of the oscillating body bearing 22 Is fitted with a gap fit. Therefore, the rigidity of the external gear 21 and the outer ring 22a of the oscillating body bearing 22 is lower than that of the first gear device 10, and the spring constant is smaller.

On the other hand, since the tightening allowance δ2 is smaller than the tightening allowance δ1 of the first gear device 10, the lubricant in the fitting portion between the external gear 21 and the outer ring 22a of the oscillating body bearing 22 is smaller than that of the first gear device 10. Lubrication is improved. In the present embodiment, since the fitting portion is a gap fitting, the lubrication state here is further improved. Therefore, the amount of the lubricant sealed in the seal space S is smaller than that of the first gear device 10. When the fitting portion is provided so as to suppress the occurrence of fretting as described above, the amount of the lubricant to be sealed can be further reduced. As a result, as compared with the first gear device 10 having a larger tightening allowance δ1, the stirring loss of the lubricating oil during operation is relatively small, and the power transmission efficiency is improved.

[Technical effect of this embodiment]
As described above, according to the present embodiment, the tightening allowance δ1 between the external gear 11 in the first gear device 10 and the outer ring 12a of the oscillating body bearing 12 is the external gear 21 in the second gear device 20. It is different from the tightening allowance δ2 between the and the outer ring 22a of the exciter bearing 22.
That is, the spring constant and the power transmission efficiency can be adjusted by making the tightening allowance between the external gear and the outer ring of the oscillating body bearing different between the first gear device 10 and the second gear device 20. Specifically, by increasing the tightening allowance, the spring constant can be increased although the power transmission efficiency is lowered, and by reducing the tightening allowance, the power transmission efficiency can be improved although the spring constant is reduced.
Therefore, it is possible to obtain the desired performance of the spring constant and the power transmission efficiency by changing only the minimum parts related to the tightening margin without requiring a large change of parts such as a change of the tooth profile. As a result, a gear device having a desired performance can be provided at a low cost. Specifically, the first gear device 10 can be provided for applications that emphasize the spring constant, and the second gear device 20 can be provided for applications that emphasize power transmission efficiency.

[Other]
Although the embodiment of the present invention has been described above, the present invention is not limited to the above embodiment.
For example, in the above embodiment, the first gear device 10 and the second gear device 20 share the same components (same shape and dimensions) that are not related to the tightening allowance between the external gear and the outer ring of the oscillating body bearing. It was decided that it was configured. However, the first gear device 10 and the second gear device 20 may have different shapes of other members as long as the internal gears have at least the same shape.
Further, in the above embodiment, the tightening allowance δ1 of the first gear device 10 is a positive value, and the tightening allowance δ2 of the second gear device 20 is a negative value. However, the tightening allowance δ1 and the tightening allowance δ2 may be different from each other.

Further, in the above embodiment, the tubular meshing gear device has been described as an example as the first gear device 10 and the second gear device 20. However, the flexible meshing type gear device according to the present invention is not limited to the tubular type, and may be a cup type, a top hat type, or the like.
In addition, the details shown in the above-described embodiment can be appropriately changed without departing from the spirit of the invention.

In the above description, the present invention has been described from the viewpoint of a series (product group) of gear devices including a plurality of gear devices, but the present invention describes how to construct and design each gear device included in the series. From this point of view, it can be regarded as a method of constructing or designing a series of gear devices (gear device group). Further, from the viewpoint of how to manufacture a series of gear devices (gear device group) including a plurality of gear devices, it can be regarded as a manufacturing method of a series of gear devices (gear device group).

10 1st gear device 11 External gear d11 Inner diameter δ1 Tightening allowance between the external gear and the outer ring of the exciter bearing 12 Exciter bearing 12a Outer ring d12i Inner diameter d12o Outer diameter 12b Rolling element 12c Cage PCD1 Pitch circle diameter 20 Second gear device 21 External gear d21 Inner diameter δ2 Tightening allowance between the external gear and the outer ring of the exciter bearing 22 Exciter bearing 22a Outer ring d22i Inner diameter d22o Outer diameter 22b Rolling element 22c Cage PCD2 Pitch circle diameter 30 Exciting body shaft 30A Exciting body 31G 1st internal gear 32G 2nd internal gear O1 Rotating shaft S Seal space

Claims (8)

A series of gear devices including a first gear device and a second gear device.
Each of the first gear device and the second gear device is between an internal gear, an external gear, a oscillating body that bends and deforms the external gear, and the external gear and the oscillating body. It is a flexible meshing type gear device having a oscillating body bearing arranged in.
In the first gear device and the second gear device, at least the internal gears have the same shape, and the tightening allowances between the external gear and the outer ring of the oscillating body bearing are different from each other.
A series of gear devices. The first gear device and the second gear device have different outer diameters of the outer rings of the exciter bearing.
The series of gear devices according to claim 1. The first gear device and the second gear device have different outer diameters of the cages of the oscillator bearings.
The series of gear devices according to claim 2. The first gear device and the second gear device have different outer peripheral lengths of the exciter.
The series of gear devices according to claim 2 or 3. In the first gear device and the second gear device, the rolling elements of the oscillating body bearing have the same shape as each other.
The series of gear devices according to any one of claims 2 to 4. The first gear device and the second gear device have different amounts of lubricant sealed therein.
The series of gear devices according to any one of claims 1 to 5. A method for manufacturing a group of gear devices including a first gear device and a second gear device.
Each of the first gear device and the second gear device is between an internal gear, an external gear, a oscillating body that bends and deforms the external gear, and the external gear and the oscillating body. It is a flexible meshing type gear device having a oscillating body bearing arranged in.
In the first gear device and the second gear device, at least the internal gears have the same shape as each other.
A manufacturing process of the first gear device including a step of fitting the external gear of the first gear device and the outer ring of the exciting body bearing with a first tightening allowance, and a manufacturing process of the first gear device.
A manufacturing process of the second gear device including a step of fitting the external gear of the second gear device and the outer ring of the oscillating body bearing with a second tightening allowance different from the first tightening allowance. , With
Manufacturing method of gear group. It is a design method of a gear device group including a first gear device and a second gear device.
Each of the first gear device and the second gear device is between an internal gear, an external gear, a oscillating body that bends and deforms the external gear, and the external gear and the oscillating body. It is a flexible meshing type gear device having a oscillating body bearing arranged in.
In the first gear device and the second gear device, at least the internal gears have the same shape as each other.
The distance between the external gear of the first gear device and the outer ring of the exciting body bearing is set as the first tightening allowance.
The external gear of the second gear device and the outer ring of the oscillating body bearing are set to a second tightening allowance different from the first tightening allowance.
How to design a group of gears.

Images