JPS6223169B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a bearing device for a universal joint, in particular a method for lubricating the sliding surface between the trunnion end face of a spider and the inner bottom face of a bearing case that is brought into sliding contact with the spider trunnion end face with an appropriate preload. Concerning sexual improvement.

This type of bearing device has a grease reservoir 2 with a diameter of 2Ri on the inner bottom surface of a solid type or shell type bearing case 1 as shown in FIG.
Sliding surface 3 consisting of an annular flat surface with Ri and outer diameter 2Ro
is formed, and the trunnion is used with an appropriate preload or clearance provided between the sliding surface 3 and the end face of the trunnion.

However, in recent years, the speed of equipment has increased, and with a configuration in which a gap is provided between the sliding surfaces, it is difficult to balance the universal joint and cause vibrations. There is an increasing tendency to use a preloaded state in which the surfaces are pressed together, even with a large preload applied. However, increasing the speed of equipment inevitably increases the sliding speed in the oscillating motion between the sliding surfaces, and this increase in sliding speed and increase in the preload increases the load on the bearing, and the sliding surface There is a drawback that lubrication between the two surfaces is insufficient, accelerating wear on the sliding surfaces and causing premature seizure, and countermeasures are strongly required.

The present invention provides a bearing device as described above, which is configured to reliably supply lubricant between the sliding surfaces that reciprocate with each rotation of the universal joint, and to improve the lubrication effect. The aim is to significantly improve the

This invention will be described in detail with reference to Examples below. Second
In the figure, the shafts 5 and 6 are arranged parallel to each other with different centers, and the shaft 7 connects the shafts 5 and 6 via universal joints 8 at both ends, and between the shafts 5 and 7 and between the shafts 6 and 7, respectively. When the installation angle θ exists, for one rotation of the universal joint 8, the relative 1 in the circumferential direction between the sliding surfaces of the trunnion end face and the inner bottom face of the bearing case
A reciprocating rocking motion is generated twice, and the rocking angle is twice the mounting angle θ, that is, 2θ. Therefore, the relative swing amount of both sliding surfaces at an arbitrary radial position R is temporarily set as 2θ×R.

3, 4, and 5 are views showing an example of the case where the present invention is implemented on the sliding surface 3 of the inner bottom surface of the bearing case 1, and the invention is applied to the entire surface of the sliding surface 3. A large number of circular recesses 11 are formed which are discontinuous in the circumferential direction and the radial direction, and the maximum arch width B of the convex part 10 in the circumferential direction formed between the recesses 11 is the same as that at the radial position R. Relative swing amount of sliding surface 2
The position and diameter D of the recess 11 are determined so as to always satisfy a width B2θ×R that is not larger than θ×R (arc). Note that the amount of rocking 2θ×R of the sliding surface at any radial position R increases dimensionally from the inner diameter side to the outer diameter side of the sliding surface 3, so in the embodiment, the recessed portion The diameter D of 11 is made larger from the inner diameter side to the outer diameter side of the sliding surface 3 within a range that satisfies the condition B2θ×R. Further, the depth t of the recess 11 is 0.1 to 0.3.
Although it is preferable that the depth t be approximately mm, the depth t is not particularly limited. Thus, the sliding surface 3 has a convex portion 10 that comes into sliding contact with the trunnion end surface (not shown).
An uneven surface having a concave portion 11 serving as a lubricant reservoir is formed on the circumferential surface thereof.

In the above embodiment, a case has been described in which the sliding surface 3 formed on the inner bottom surface of the bearing case 1 is made into an uneven surface by forming a large number of recesses 11. The surface 3 may be a flat surface, and the recessed portion may be formed in the end surface of the trunnion (not shown) to form the uneven surface as described above.

In addition, in order to reduce the surface pressure per unit area of the sliding surface 3, the area of the convex portion 10 is set as B2θ×
It is desirable to form the recess 11 so that it is as large as possible within the range that satisfies the condition R. Furthermore, the shape of the recess 11 does not need to be limited to a circular shape;
It can be made into any shape such as a polygonal shape such as a triangle, quadrangle, or hexagon, or an ellipse.

In addition, Fig. 3, Fig. 4, and Fig. 5 are based on the assumption that the diameter D
A large number of recesses 11 with a diameter D′, a large number of recesses 11 with a diameter D′,
In the case where a large number of recesses 11 with diameters D'' are arranged on each concentric circle, when the sliding surface 3 swings at an angle 2θ, each recess 11 with diameters D and D', the diameter
The concave portions 11 of D' and D'' are configured so that their respective rocking trajectories overlap as shown by the radial dimensions r and r', and the convex portion 10 formed between the concave portions 11 The arc width B, B', B'' in the circumferential direction at any radius R, R', R'' position is B2θ×R,
The pitch interval and diameter D in the circumferential direction of the recessed portion 11 are set such that B′2θ×R′ and B″2θ×R″ are satisfied.
Set D', D'' and radially overlapping dimensions r, r' or diameters of concentric circles.

Furthermore, in the above, the recesses 11 do not necessarily need to be arranged concentrically, but may be arranged randomly, and the diameters D, D', and D'' of each recess 11 are not necessarily large enough to reach the outer diameter side of the sliding surface 3. It does not have to be the same diameter.

The present invention has the above-described configuration, and as shown in FIG.
In sliding contact with the universal joint, the sliding surfaces 3 and 40 perform a relative reciprocating motion of angle 2θ in one rotation of the universal joint, and at any radius R position, 2θ×R
When the swing width is , the maximum arc width B of the convex portion 10 in the circumferential direction is set to be B2θ The end face is
It moves forward on the sliding surface 40 by a distance 2θ×R from position B indicated by a solid line to position B ₁ indicated by an imaginary line, and
In the second half of the rotation, it moves back from B ₁ to the position shown by B.
That is, the positions B and _B1 are different positions on the sliding surface 40 that do not overlap due to the relationship of B2θ×R, and each recess 11 is also located on the sliding surface 40 in the first half of one rotation. Move to a different position and return in the second half. Therefore, each of the recesses 1 that holds the lubricant
1, the entire surface of the sliding surface 40 of the mating member is wetted with lubricant by the oscillating motion of 2θ×R for each rotation of the universal joint, and both sliding surfaces 3 and 40 are wetted with lubricant for each rotation of the universal joint. Each rocking motion ensures lubrication.

On the other hand, as shown in FIG. 3, the sliding surface 3 has an uneven surface in which the recesses 11 are discontinuous in the circumferential direction and the radial direction, and the maximum of the convex parts 10 formed between the many recesses 11 is In order to set the arc width B to B2θ×R, it is necessary to pay attention to not only the arrangement pitch of the recesses 11 in the circumferential direction but also the arrangement pitch in the radial direction. In other words, the radius of a circle circumscribing the recesses 11 arranged on an outer concentric circle on the inner diameter side of the sliding surface is circumscribed on the outer diameter side of the sliding surface with respect to the recesses 11 arranged on an inner concentric circle. By setting r smaller than the radius of the circle as shown in FIG. 7, the locus of the oscillating movement of the inner recess 11 in the oscillating movement of 2θ×R in one rotation of the universal joint. On the other hand, the trajectories of the rocking movements of the outer concave portions 11 always overlap as shown by the imaginary line 11' in the figure, and the maximum arc width B of the convex portions 10 is never larger than the amount of rocking 2θ×R at any radial position. Also in the radial direction of the sliding surfaces 3 and 40, the sliding surfaces 40 are wetted with the lubricant held in the recesses 11 to lubricate the entire surface. Therefore, in this case as well, the sliding surfaces 3, 40 are reliably supplied with lubricant every time the universal joint rotates.

Further, the amount of swinging 2θ×R of the sliding surface at any radial position R increases from the inner diameter side to the outer diameter side of the sliding surface, and furthermore, one swinging movement causes the convex surface of the sliding surface to In order to ensure that all parts are wetted with the lubricant held in the recess, and to facilitate design and processing, the recess is formed to have a larger diameter from the inner diameter side to the outer diameter side of the sliding surface. It is desirable to do so.

In other words, this invention reliably supplies lubricant between the sliding surfaces of the trunnion end surface and the inner bottom surface of the bearing case, which are in sliding contact under a preload, each time the universal joint rotates, thereby improving its lubrication performance. greatly improves the performance and prevents wear and seizure,
The life of the bearing device is greatly improved and the universal joint becomes maintenance-free, and recesses discontinuously formed in the circumferential direction and the radial direction are formed on the sliding surface. By configuring the sliding surface to be an uneven surface, it is possible to increase the contact area between both sliding surfaces as much as possible, reducing the surface pressure per unit area and improving its wear resistance. , and the strength against bearing loads can be improved.

[Brief explanation of the drawing]

FIG. 1 is a longitudinal cross-sectional view showing a schematic configuration of a bearing device according to the present invention, FIG. 2 is a front view showing the mounting angle of the universal joint, FIG. 3 is an enlarged plan view of the main part of the invention, and FIG. The figures are an enlarged sectional view taken along the - line in Fig. 3, Fig. 5 is a plan view further enlarged from Fig. 3, and Figs. 6 and 7 are an enlarged sectional view and a plan view for explaining the operation. 1...Bearing case, 3...Sliding surface, 4...Trunion, 5, 6, 7...Shaft, 8...Universal joint, 10...Protrusion, 11...Concave part, 40...Sliding Surface, θ...Installation angle, B, B',
B″…Circumferential width (arc) of the convex portion, R, R′, R″…
...any radius.

Claims (1)

[Claims] 1. On one of the sliding surfaces where the trunnion end surface of the spider and the inner bottom surface of the bearing case slide,
A large number of recesses that are discontinuous with each other in the circumferential direction and radial direction are formed, and the recesses are arranged on a plurality of concentric circles, and among the recesses arranged on the plurality of concentric circles, they are arranged on the outer concentric circle. The diameter of the circle that circumscribes the recess on the inner diameter side of the sliding surface is set smaller than the diameter of the circle that circumscribes the recess on the outer diameter side of the sliding surface arranged on the concentric circle inside the recess, and each recess is The maximum arc width B in the circumferential direction of the convex portion formed between is
Swing amount 2 between the sliding surfaces at any radius R position given by the mounting angle θ of the universal joint
A bearing device for a universal joint, characterized in that the recessed portion is formed so that B≦2θ×R with respect to θ×R. 2. The bearing device according to claim 1, wherein a large number of recesses discontinuous with each other in the circumferential direction and the radial direction are formed in the sliding surface in a random arrangement. 3. A patent in which a number of recesses discontinuous with each other in the circumferential direction and radial direction are formed on the sliding surface such that the diameter of the recesses increases from the inner diameter side to the outer diameter side of the sliding surface. A bearing device according to claim 1 or 2. 4. The bearing device according to any one of claims 1 to 3, wherein a large number of recesses that are discontinuous with each other in the circumferential direction and the radial direction are formed on the inner bottom surface of the bearing case. 5. The bearing device according to any one of claims 1 to 3, wherein a large number of recesses that are discontinuous with each other in the circumferential direction and the radial direction are formed on the end face of the trunnion.