JPS6131539Y2 - - Google Patents

Description

[Detailed explanation of the invention] This invention is a rolling bearing that extends the life of the bearing.
In particular, it relates to a rolling bearing assembly in which the maximum rolling element load and concentrated stress are reduced by bending and deforming the bearing ring.

Rolling bearings are generally used with the outer ring fixed to the housing and the inner ring fixed to the shaft, but when the outer ring is used with a fixed load acting on the outer ring and the inner ring receiving a fixed load, when the inner ring is used with a fixed rolling load, The load on the bearing is transmitted from the shaft to the housing via the rolling bearing, and a load zone is formed depending on the magnitude and direction of the load.

In a conventional rolling bearing, as shown in FIG. 1, a rolling bearing 4a is attached to a housing 7a by an outer ring 1a, and an inner ring 2a fixedly supports a shaft 6a via rolling elements 3a to rotate. The raceway surfaces 11a and 21a of the outer ring 1a and the inner ring 2a are mutually concentric circular orbits centered on the axis Pa, and the rolling elements 3a are arranged between the concentric circular orbits. ing. (In order to avoid complication in the drawing, the cage is omitted from the illustration.) However, in the case of the above-mentioned conventional bearing structure having circular bearing rings concentric with the outer and inner rings, the load range (indicated by the dashed line in the figure) under load is is small, the load is concentrated in the center of the load zone, and the load distribution is not averaged. Therefore, extremely large concentrated stress occurs between the rolling elements 3 and the bearing ring.

In general, metal fatigue, which progresses due to concentrated stress on the raceway surface caused by rolling elements, is the biggest factor limiting the life of rolling bearings, and the fatigue life of rolling bearings is inversely proportional to the stress to the 9th or 10th power. Therefore, it is known that reducing this stress even slightly will greatly extend the fatigue life.

As a special method to eliminate these drawbacks of conventional rolling bearings, the fitting surface of the housing is made slightly oval, or a partial step is provided on the fitting surface of the housing to create a gap. A known method is to use a ring to elastically deform the bearing ring on the load side into an elliptical shape when the bearing is loaded. However, among these methods, machining the housing into an oval shape is extremely difficult and incompatible, and in the case of a ring with a step, it is difficult to fit around the boundary between contact and non-contact with the raceway. Since it has drawbacks such as stress concentration on the mating surfaces and easy wear and cracking, it is rarely put into practical use or is only used for very special purposes.

This idea eliminates the above-mentioned drawbacks and problems, provides compatibility, and expands the range of applications.In order to expand the load range, it reduces the maximum rolling element load (Qmax) and extends the life of rolling bearings. The objective is to prevent skidding (abnormal damage caused by the sliding phenomenon of rolling elements) during high-speed rotation.

Next, the rolling bearing assembly of this invention will be explained with reference to the embodiments of the ball bearing shown in Figs. 2 to 12. Figs. The figure shows a first embodiment according to this invention, in which a rolling bearing 4 has an outer ring 1.
It is attached to the housing 7 via a circular ring 5 fitted to the outer periphery of the inner ring 2, and is configured to support the load and rotation of the shaft 6 fitted to the inner ring 2. Said circular ring 5
The inner peripheral surface is provided with one relief part 8, and the relief part 8 has a crescent-shaped groove 81 having an appropriate length, width, and depth in the circumferential direction, and the groove 81 is plated or plated. A raceway ring (outer ring 1,
The housing 7 is configured by a deformable member 83 having a smaller elastic constant than the inner ring 2) and the circular ring 5, and the housing 7 is
is installed on.

Furthermore, in FIG. 3, A-A in FIG.
Although this is a partial cross-sectional view in the direction, it shows that the concave groove 81 of the circular ring 5 is formed to have a uniform depth in the axial direction at any position in the circumferential direction.

In the rolling bearing assembly constructed in this way, when a load P from the shaft 6 fitted to the inner ring 2 acts on the inner ring 2 (lower part of the figure), and further acts on the outer ring 1 while the rolling elements 3 rotate. , the deformable member 83 formed in the concave groove 81 of the circular ring that is in contact with this is deformed, and the outer ring raceway surface 11 of the outer ring 1 is also slightly bent and deformed into an elliptical shape, and the effect of the load P on its long axis direction The directions are almost the same, and the outer ring raceway surface 11
The load range of the load P acting on the housing 7 due to the deformation of is shown by the two-dot chain line in Figure 2, and the load is much more averaged and the range is expanded compared to the conventional load range (the one-dot chain line in Figure 1). Therefore, the maximum rolling element load (Qmax) is also lower than before.

Next, FIG. 4 is a sectional view corresponding to FIG. 3 showing a second embodiment of this invention which is a modification of the first embodiment, and shows the concave groove 81 in the first embodiment in the circumferential direction of the circular ring 5. It is crescent-shaped and formed only in the center in the axial direction,
This part is filled and fixed with a deformable member.
In this case, the load P from the shaft 6 expands in the axial direction as well as the load range in the first embodiment described above, and the maximum contact pressure on the load side raceway ring (outer ring in this case) due to the rolling element load Q (p max) can be made small.

FIG. 5 is also a cross-sectional view corresponding to FIG. 3 showing a third embodiment of this invention which is a modification of the first embodiment, and similarly to the second embodiment, the concave groove 81 is formed in a crescent shape in the circumferential direction of the circular ring 5. In the axial direction, it has a T-shaped cross section with a thick wall only at the central portion, and a deformable member 83 is filled and fixed in this portion.

Furthermore, FIG. 6 shows a fourth embodiment of this invention, in which a relief part 8 consisting of a groove 81 and a deformable member 83 in the first embodiment is formed on the outer peripheral surface of the circular ring 5. In the example, relief portions 8 are provided at two symmetrical positions, one on the load area side of the load P from the shaft 6 and the other on the opposite load area side. In this example, the load P
When the deformable member 83 is deformed, the circular ring 5 is also deformed, and the outer ring 1 and the outer ring raceway surface 11 are deformed via the circular ring 5. The rolling bearing assembly having the two relief portions 8 is also effective for bearing devices in which the load direction alternately changes up and down, such as rolling roll bearings.

Moreover, FIG. 7 shows a fifth embodiment of this invention,
On the outer periphery of the outer ring 1 on the load zone side, as described above, one relief part 8 is formed in the circumferential direction by the crescent-shaped groove 81 and the deformable member 83, and the relief part 8 is aligned with the housing position in the direction of the load P from the shaft 6. The outer ring 1 is attached to the outer ring 1.

FIG. 8 shows a sixth embodiment of this invention, in which a hollow hole 82 is provided in the ring 5 instead of the groove 81 described above, and the ring 5 has an arc-shaped hollow extending in the circumferential direction. A hole 82 is opened in the axial direction, and the above-described deformable member 83 is filled and fixed inside the hollow hole 82 to form a relief portion 8. FIG. 9 shows a partial sectional view taken along the line B--B in FIG. 8.

Furthermore, FIG. 10 shows a seventh embodiment of this invention, in which a circular ring 5 is connected to a main body portion 51 and an arcuate member 52.
A concave groove 81 is formed in a part of the plane of the arcuate member 52 that joins to the main body member 51, and the above-described deformable member is filled and fixed in this part and combined with the main body member 51. It is designed to be used.

11 and 12 show a rolling bearing assembly for an outer ring rotating load, and FIG. 11 shows an eighth embodiment of this invention, in which an inner ring 2 is connected to a fixed load side shaft 6 via a circular ring 5 is fitted, and a housing 7 on the rotating load side is attached to the outer ring 1. The load P on the housing 7 is applied from the outer ring 1 and the rolling elements 3 to the shaft 6.
It acts on the circular ring 5 fixed to the side, and the outer peripheral surface of the circular ring 5 has a crescent-shaped concave groove 81 in the circumferential direction similar to the first to fifth embodiments described above. In the concave groove part 81, a deformable member 83 is filled and fixed in the same manner as described above to form a relief part 8, which is mounted on the shaft 1 in a position in the direction of the load P (on the upper side of the shaft).

FIG. 12 shows a ninth embodiment of this invention, in which the circular ring 5 is provided with a hollow hole 82 similar to the fifth embodiment described above in place of the groove 81 in the eighth embodiment. It is something.

As mentioned above, in the rolling bearing assembly according to this invention, the fixed load side bearing ring or the circular ring 5 attached to the fixed load side bearing ring has at least one relief part 8, so that the shaft 6 or the housing 7 has at least one relief part 8. When a load P from the rotating side member acts, the load side (fixed load side ) By giving the bearing ring an elliptical elastic deformation, the load range on the fixed side housing 7 and shaft 6 is increased, and the maximum rolling element load (Qmax) and maximum contact pressure (pmax) are reduced. This not only extends the fatigue life of the rolling bearing 4, but also prevents abnormal damage to the rolling elements due to skidding during high-speed rotation by expanding the load range.

In addition, in this invention, the above-mentioned relief is formed at at least one location of the housing 7 or the load side (fixed load side) bearing ring with respect to the circular ring 5 or the shaft 6, or the circular ring fitted to the bearing ring. Not only in the case where the part is formed by a hollow hole 82 but also in the case where it is formed by a concave groove as shown by the reference numeral 81, the elastic Because of the deformation, the contact surface is increased compared to the conventional one without an elastic deformation member, and therefore, friction due to local stress increase near the boundary between the contact part and the non-contact part is increased compared to the conventional one without a deformation member. Cracks are less likely to occur.

In other words, by filling and fixing the deformable member in the relief part, the deformation of the shaft, housing, circular ring, etc. does not change suddenly at the relief part. The boundary between the easily deformable part and the hard to deform part becomes unclear, and friction and cracks are less likely to occur at this boundary.

Furthermore, by using a synthetic resin impregnated with a lubricant for the deformable member 83 that is filled and fixed in the groove 81, the contact surface of the mating member that comes into contact with the deformable member 83 can be effectively lubricated, thereby preventing wear caused by minute slips. effective.

Furthermore, in the present invention, when installing the raceway ring or circular ring 5 having the relief part 8, the installation is the same as in the conventional method except that the bearing ring or the circular ring 5 having the relief part 8 is aligned with the load direction position, and the circular ring 8 is When used, the circular ring 5 and the rolling bearing 4 can be made into a unit to provide compatibility, which facilitates handling.

Although the above embodiments have been explained using ball bearings, they can also be applied to other rolling bearings.

In addition, the number, position, shape, and dimensions of relief portions 8 provided in the raceway ring or circular ring 5 of the bearing, and the deformable member 8
The fixing method in 3 can of course be used within the above embodiments, and may be modified as appropriate within the scope of the claims. Select to obtain optimum performance. Particularly, as a method of partially fixing the deformable member 83 to the escape part 8, it is effective to fix the deformable member 83 to both ends of the groove 81 in the circumferential direction, for example, and form the central part as a space.

Further, as an application example of this invention, for example, the grooves 81 of the second and third embodiments may be provided in the entire circumferential range of the raceway ring or the circular ring as necessary. All or part of the groove 81 may be filled and fixed with the deformable member 83.

[Brief explanation of the drawing]

FIG. 1 is a cross-sectional view showing a conventional rolling bearing assembly, and FIGS. 2 to 12 are cross-sectional views of an embodiment using a ball bearing of this invention. FIG. 2 is a first embodiment, and FIG. 2 is a sectional view taken along line A-A, FIG. 4 is a view corresponding to FIG. 3 showing the second embodiment, and FIG.
FIG. 3 is a diagram corresponding to an embodiment, FIG. 6 is a fourth embodiment, FIG. 7 is a fifth embodiment, FIG. 8 is a sixth embodiment,
FIG. 9 is a sectional view taken along line B-B in FIG.
Figure 0 shows the 7th embodiment, Figure 11 shows the 8th embodiment, and the 1st embodiment.
FIG. 2 shows the ninth embodiment. In the symbols of the embodiments, 1 is an outer ring, 2 is an inner ring, 3 is a rolling element, 4 is a rolling bearing, 5 is a circular ring, 6 is a shaft, 7 is a housing, 8 is a relief part, 81 is a groove, and 82 is a hollow part. The hole 83 is a deformable member.

Claims (1)

[Claims for Utility Model Registration] (1) In a rolling bearing that supports a radial load, at least one portion of a bearing ring or a circular ring fitted to the bearing ring is subjected to a load in the radial direction. A deformable member that is provided with a recessed groove or a hollow hole to produce a slight deflection when the recessed part is formed, and the recessed part is made entirely or partially of a metal or synthetic resin having an elastic constant smaller than that of the bearing ring or circular ring. 1. A rolling bearing assembly characterized in that the rolling bearing assembly is filled and fixed, and is mounted and used with the relief portion located on the load zone side. (2) Claim 1 of the Utility Model Registration Claim provides a rolling bearing assembly in which the relief portion provided in the bearing ring or circular ring is a groove formed on the outer circumferential surface or inner circumferential surface of the bearing ring or circular ring. Three-dimensional. (3) In claim 1 of the utility model registration claim, the relief part provided in the bearing ring or circular ring is an arc-shaped relief part that is opened in the axial direction of the bearing ring or circular ring and extends in the circumferential direction. A rolling bearing assembly with a hollow hole.