Patent Application
20210324948
The present invention relates to a wave generator of a strain wave gearing, and more particularly relates to a wave generator provided with a wave bearing having a small friction torque.
A strain wave gearing is provided with a rigid internally toothed gear, a flexible externally toothed gear and a wave generator. The externally toothed gear is flexed radially by the wave generator and is partially meshed with the internally toothed gear. Rotation of the wave generator causes the meshing positions between the both gears to move in a circumferential direction, whereby relative rotation between the gears is generated due to the difference in the number of teeth therebetween.
A wave generator is commonly provided with a rigid plug having an elliptical contour and a deep-groove-bearing type wave bearing mounted on the outer circumferential surface of the rigid plug. The wave bearing, which is flexed elliptically by the rigid plug, is provided with outer and inner races that are flexible in a radial direction and a plurality of balls mounted between these races in a rollable state. The wave bearing is fitted inside the externally toothed gear to hold the externally toothed gear and the rigid plug in a state in which the gear and the plug can rotate relative to each other. Strain wave gearings can be divided into three types: flat type, cup type and top-hat types, according to the shape of the flexible externally toothed gear. These types of strain wave gearing are disclosed in Patent documents 1, 2 and 3.
In an example of a strain wave gearing, the wave generator is set to be a rotation input element, and an internally toothed gear or an externally toothed gear is set to be a reduced-speed rotation output element. The rigid plug rotates while radially deforming the respective parts of the wave bearing and the externally toothed gear. The inner race of the wave bearing rotates together with the rigid plug at a high speed, while the outer race thereof rotates together with the externally toothed gear. The balls, which are inserted between the inner and outer races, roll along the raceway surfaces of the inner and outer races. The wave bearing allows the rigid plug and the externally toothed gear to smoothly rotate relative to each other.
In a conventional wave bearing, the outer-race raceway surface and the inner-race raceway surface are set to be a concave surface having the same radius of curvature. The present inventors et al have made a proposal in Patent document 4 to attain an extended service life of the wave bearing of a strain wave gearing, in which the wave bearing rotates while being repeatedly flexed in the radial direction. In this proposal, the ball diameter of the wave bearing is set to dimensions 5 to 15% greater in relation to the dimensions of each model of the currently available product, and the ratio (inner-race conformity) of the inner-race raceway-surface radius and the ball diameter and that (outer-race conformity) of the outer-race raceway-surface radius and the ball diameter are both set 0.8 to 2% less than those ratios in each model of the currently available product.
Patent document 1: JP 05-172195 A
Patent document 2: JP 08-166052 A
Patent document 3: JU 02-91238 A
Patent document 4: JP 2010-164068 A
There are cases in which it is desirable to reduce the friction torque of the wave bearing in order to improve the performance of a strain wave gearing such as reduction in starting toque thereof. In view of this point, an object of the present invention is to provide a wave generator provided with a wave bearing having a low friction torque.
In the wave bearing of a currently available product, in which the balls inserted between the inner and outer races roll while the inner and outer races are repeatedly flexed in the radial direction, the outer race has a much longer theoretical service life than the inner race. The present inventors have paid attention to this fact and make the outer-race conformity large to reduce the friction torque of the wave bearing.
Specifically, according to the present invention, there is provided a wave generator of a strain wave gearing configured so that the wave generator flexes a flexible externally toothed gear into an elliptical shape to partially mesh with an internally toothed gear and moves meshing positions between the both gears in a circumferential direction, the wave generator having:
a rigid lug and a wave bearing,
wherein the wave bearing is provided with an annular outer race that is flexible in a radial direction thereof, an annular inner race that is flexible in a radial direction thereof, and a plurality of balls inserted between the outer race and the inner race;
the wave bearing is mounted on an elliptical outer circumferential surface of the rigid plug to flex the outer race and the inner race into an elliptical shape; and
where D is a ball diameter of the balls, Ro is a raceway-surface radius of the outer race, Ri is a raceway-surface radius of the inner race, Ro/D is an outer-race conformity, and Ri/D is an inner-race conformity,
the outer-race conformity Ro/D is greater than the inner-race conformity Ri/D.
In the present invention, the raceway-surface radius (radius of curvature) Ro of the outer-race raceway surface is greater than the raceway-surface radius (radius of curvature) Ri of the inner-race raceway surface. In comparison with a case in which the raceway-surface radius of the outer-race raceway surface is the same as that of the inner-race raceway surface (in other words, when the outer-race conformity is the same as the inner-race conformity), the balls become easier to make relative motion with respect to the outer-race raceway surface, whereby reducing friction force generated between the balls and the outer-race raceway surface. As a result, it is possible to obtain a wave bearing having a low friction torque as a whole. Here, when the outer-race conformity is made large, the theoretical service life of the outer race becomes short. When the outer-race conformity is the same as the inner-race conformity as in the conventional case, the theoretical service life of the outer race is longer than that of the inner race. It is possible to reduce the friction torque of the wave bearing while maintaining the practical service life thereof to be the same level as in the conventional case by setting the outer-race conformity in an appropriate manner.
There is a case in which the inner race of the wave bearing is integrated in the elliptical outer circumferential surface of the rigid plug and an inner-race raceway surface is formed on the elliptical outer circumferential surface. The present invention can also be applied to such a case as this.
In a conventional wave bearing, the outer-race conformity is in a range from 51.1% to 52.3% and the inner-race conformity is 51.5% to 52.5%. In this case, the theoretical service life of the outer race is longer than that of the inner race as indicated by the following formula.
L10 outer race/L10 inner race≈2.5 to 3.1
In the present invention, when the inner-race conformity is in a range from 51.1% to 52.3% as in a conventional case, the outer-race conformity is desirably set to be in a range from 52.6% to 58.1%. By doing so, the theoretical outer-race service life becomes close to be the theoretical inner-race service life or even to be the same as that, and it is therefore possible to reduce the friction torque of the wave bearing while maintaining the practical service life thereof as the same level as of a conventional case.
An embodiment of a strain wave gearing according to the present invention will be described hereinbelow with reference to the drawings. The present invention is applied to a cup type strain wave gearing in the following embodiment. The present invention can also be applied to a wave generator of a top-hat type or a flat type strain wave gearing in a similar manner.
The wave generator 4 is linked to a motor shaft or other high-speed rotation input shaft. When the wave generator 4 rotates, the meshing positions of the both gears 2 and 3 move in the circumferential direction, whereby a relative rotation between the both gears 2 and 3 is generated due to the difference in the number of teeth therebetween. For example, the internally toothed gear 2 is fixed not to rotate and the externally toothed gear 3 is linked to a member on the load side. A reduced-speed rotation is taken out from the externally toothed gear 3 and is transmitted to the member of the load side.
The wave bearing 7 is flexed into an elliptical shape by the rigid plug 5 and, in this state, is fitted into the externally toothed gear 3, whereby maintaining a state in which the externally toothed gear 3 is rotatable relative to the rigid plug 5 lined to a high-speed rotation input shaft. The inner race 8 is formed on the outer circumferential surface with an inner-race raceway surface 11 and the outer race 9 is formed on the inner circumferential surface with an outer-race raceway surface 12. The balls 10, which are inserted between the elliptically flexed inner and outer races 8 and 9, perform a rolling motion along the inner-race raceway surface 11 and the outer-race raceway surface 12, so that the rigid plug 5 and the externally toothed gear 3 can smoothly rotate to each other with a small torque.
More specifically, the wave bearing 7 is flexed into an elliptical shape by the rigid plug 5. Where Lmax is the major axis of the elliptical shape and Lmin is the minor axis thereof, one or a plurality of balls 10 located on both ends of the major axis Lmax are a tight ball 10a. The tight ball 10a performs a rolling motion while being maintained in a tight state. In the tight state, the ball is sandwiched with a certain pressing force between the inner-race raceway surface 11 and the outer-race raceway surface 12 and is in a point contact with the inner-race raceway surface 11 and the outer-race raceway surface 12. The remaining balls 10, which are located on the portions other than the both ends of the major axis Lmax, are a loose ball 10b. The loose ball 10b is in a loose state in which a gap is formed at least between the loose ball and the inner-race raceway surface 11 or between the loose ball and the outer-race raceway surface 12 so as to perform a free rolling motion.
As illustrated in
Here, D is a ball diameter, Ri is a raceway-surface radius of the inner-race raceway surface 11, and Ro is a raceway-surface radius of the outer-race raceway surface 12. The ratio Ri/D of the inner-race raceway-surface radius Ri and the ball diameter D is called as an inner-race conformity, and the ratio Ro/D of the outer-race raceway-surface radius Ro and the ball diameter D is called as an outer-race conformity. The outer-race conformity Ro/D is greater than the inner-race conformity Ri/D. In this example, these parameters are set as in Table 1.
According to experiments conducted by the present inventors et al, it was confirmed that the friction torque of the wave bearing 7 can be reduced while maintaining the practical service life thereof to be the same level as in a conventional one by setting the outer-race conformity to be a value within the above-mentioned range.
A strain wave gearing 20 is provided with a rigid internally toothed gear having a first internally toothed gear 21 and a second internally toothed gear 22. The first and second internally toothed gears 21 and 22 are coaxially disposed in parallel, and a cylindrical flexible externally toothed gear 23 is disposed inside these internally toothed gears. A wave generator 24 having an elliptical contour is fitted into the externally toothed gear 23. The externally toothed gear 23 is flexed into an elliptical shape by the wave generator 24 so that the external teeth 23a thereof are meshed with both the inner teeth 21a of the first internally toothed gear 21 and the internal teeth 22a of the second internally toothed gear 22 on both ends of the major axis Lmax of the elliptical shape. For example, the number of teeth of the first internally toothed gear 21 is 2n (n is a positive integer) greater than the number of teeth of the second internally toothed gear 22, and the number of teeth of the externally toothed gear 23 is the same as that of the second internally toothed gear 22. The external teeth 23a mesh with the internal teeth 21a and 22a on positions of the major axis Lmax of the elliptical shape of the externally toothed gear 23.
The wave generator 24 is provided with a rigid plug 25 and a wave bearing 27 mounted on the elliptical outer circumferential surface 26. The wave bearing 27 is provided with an inner-race raceway-surface 31 formed on the elliptical outer circumferential surface of the rigid plug 25, a circular outer race 29 that is flexible in the radial direction, and a plurality of balls 30. The balls 30 are mounted in a rollable state between the inner-race raceway surface 31 and an outer-race raceway surface 32 formed on the inner circumferential surface of the outer race 29.
The wave bearing 27 is flexed into an elliptical shape by the rigid plug 25 and, in this state, is fitted into the externally toothed gear 23. The wave bearing 27 holds the externally toothed gear 23 and the rigid plug linked to a high-speed rotation input shaft in a relatively rotatable state. The balls 30, which are inserted between the inner-race raceway surface 31 and the outer-race raceway surface 32, perform a rolling motion along these surfaces, which allows the rigid plug 25 and the externally toothed gear 23 can be rotated relative to each other with a small torque.
In this example as well, the wave bearing 27 has a basic structure that is the same as in a wave bearing of a deep-groove-bearing type but has the outer-race conformity larger than the inner-race conformity. For example, the inner-race conformity is set to be a value within a range from 51.1% to 52.3% and the outer-race conformity is set to be a value within a range from 52.6% to 58.1%.
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/JP2017/032380 | 9/7/2017 | WO | 00 |
