JP2003042149A - Complex rolling bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To solve the problem, relating to a rolling bearing having little friction loss in a state of being applied with a radial load and an axial load: that power loss is large in a tapered roller bearing due to friction between the end face of the large-diameter side of the tapered roller bearing and the flange face of the large-diameter side of an inner ring, and a rotational speed is necessarily limited due to the thermal generation caused by the friction; that an angular contact bearing can not bear a large load while it is suitable for a high revolution; and that, in a type where a radial bearing and a thrust bearing are used individually and loads are applied to the bearings, respectively, a structure becomes complicated and the friction loss is practically large in the thrust bearing itself, and thus a practical and sufficient effect is not obtained. SOLUTION: The complex rolling bearing is provided with a first bearing having a profile of a tapered roller bearing, and a bearing member, in which the bearing member is kept in contact with an end face 12 at a large diameter side of a tapered roller 5 of the first bearing, having a disk capable of coaxially rotating with the first bearing and also preventing the disk from moving in the axial direction.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to the technical field of rolling bearings, and more particularly, to a rolling bearing having a small friction loss in the state of receiving both radial load and axial load.

[0002]

2. Description of the Related Art Conventionally, tapered roller bearings or angular contact bearings are often used for the above applications. There is also a structure in which a radial bearing and a thrust bearing are separately used, and the weight is distributed to each.

[0003]

The taper roller bearing has a large power loss due to the friction between the large diameter side end surface of the taper roller and the large diameter side flange surface of the inner ring. there were. Further, while the angular contact bearing is suitable for high speed rotation, it has a drawback that it cannot receive a large load. In addition, the radial bearing and thrust bearing are used separately,
The structure in which the weight is dispersed has a complicated structure, and the thrust bearing itself inherently has a large friction loss, so that the practical effect is insufficient.

An object of the present invention is to provide a bearing which eliminates the above-mentioned drawbacks and can rotate at a high speed under a large load and which has a simple structure.

[0005]

The bearing of the present invention solves the above drawbacks by improving the method of supporting the end surface of the tapered roller type bearing on the large diameter side of the tapered roller.

The first means is a method in which a so-called thrust ball bearing receives the force acting on the large diameter side end surface of the tapered roller in the direction of the rotation axis of the roller. In this system, the composite rolling bearing is arranged so as to come into contact with the end surface on the large diameter side of the taper roller and the axial end surface of one disk of the thrust ball bearing.

The second means is a system in which a so-called sliding type thrust bearing receives the force acting on the large diameter side end surface of the tapered roller in the direction of the rotation axis of the roller. In this system, the composite rolling bearing is arranged so as to come into contact with the end surface on the large diameter side of the taper roller and the axial end surface of one disk of the sliding thrust bearing.

[0008]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 is a sectional view parallel to the rotation axis showing an example of an embodiment of the first means of the present invention.

In FIG. 1, a tapered cylindrical outer surface 1
A first bearing of a so-called tapered roller type, which is formed by combining an inner ring 2 having an outer ring 4, an outer ring 4 having a tapered cylindrical inner surface 3 and a plurality of taper rollers 5, and a plurality of first bearings arranged on a circumference concentric with the bearing. The second bearing, which is a so-called thrust ball bearing configured so as to be sandwiched between the ball 6 and the disks 9 and 10 having circumferential grooves 7 and 8 respectively on both sides in the axial direction across the circle, is the first bearing described above. The end surface 11 on the large diameter side of the taper roller 5 of the bearing 2 is arranged so as to abut the axial end surface 12 of the one disk 9 of the second bearing at point A. Reference numeral 13 is a collar member for fixing an axial gap between the first bearing and the second bearing and fixing it to the rotary shaft 14, and 15 is a retainer for determining the position of the taper roller by a conventional technique.

The operation of the composite rolling bearing of the present embodiment formed as described above will be described.

In the embodiment shown in FIG. 1, when a load is applied to the outer ring 4 of the first bearing, the load is transmitted to the inner ring 2 via the taper roller 5. At this time, the component force in the direction of moving to the large diameter portion acts on the taper roller 5. In the conventional bearing, this load is received by the flange portion provided on the inner ring 2. However, in the present embodiment, the inner ring 2 has no flange portion, and the end surface 11 on the large diameter side of the taper roller 5 is A. The points are arranged so as to come into contact with and receive the axial end surface 12 of the disk 9 on one side of the second bearing. In this case, the disk 9 of the end surface 11 on the large diameter side of the taper roller 5
Taper roller 5 at the contact point A with the axial end surface 12 of
The radius above is smaller than the radius of the large outline. Therefore, the rotation speed of the disc 9 and the rotation speed of the inner ring 2 are slightly different. In the conventional bearing, since the different rotational speeds are received by the point contact or the line contact with the inner ring, strong sliding friction is generated, which causes heat generation and wear. In the case of rolling contact by point contact or line contact, even if the speed difference is small, the sliding resistance is very large, so that a large friction loss occurs.
In the present embodiment, the inner ring 2 has no flange portion and is arranged so that the large-diameter side end surface 11 of the taper roller 5 abuts and receives the axial end surface 12 of the one disk 9 of the second bearing. The speed difference at the contact point between the end surface 11 on the large diameter side of the taper roller 5 and the axial end surface 12 of the disk 9 is because the second bearing forms a so-called thrust ball bearing. The bearing circumferential grooves 7, 8 can be absorbed by rotating at a relatively low speed, and the sliding motion at point A does not occur. Therefore, even if the entire bearing rotates at high speed, the friction loss is extremely small.

FIG. 2 is a sectional view parallel to the axis of rotation showing an example of the embodiment of the second means of the present invention.

In FIG. 2, the disk 29 is a collar member 13.
And slides and rotates via a slide ring 30, and the second bearing is a sliding thrust bearing. The axial end surface 32 of the disk 29 is in contact with the large diameter side end surface 11 of the taper roller 5 at a point A, and the other axial end surface 33.
Is in contact with the sliding ring 30.

The operation of the composite rolling bearing of the second embodiment formed as described above will be described.

In FIG. 2, the speed difference between the inner ring 2 and the end surface 11 of the taper roller 5 on the large diameter side at the contact point with the axial end surface 32 of the disk 29 is such that the second bearing is a so-called sliding thrust bearing. Since the second bearing is rotated at a relatively low speed, it can be absorbed.
In this case, since the sliding resistance itself is small as a feature of the sliding type bearing, when the distance between the point A and the tapered surface 1 is relatively small, the speed difference between the inner ring 2 and the disk 29 is small, and a large friction loss occurs. Does not happen. Therefore, even if the entire bearing rotates at a high speed, the friction loss is greatly reduced as compared with the conventional bearing, and the bearing can be designed substantially as compact as the conventional bearing. In FIG. 2, the inner ring 2 and the collar member 1
Although it is a separate member from 3, it does not violate the gist of the present invention even if it is integrated if the manufacturing problem is dealt with.

[0017]

As is apparent from the above description, the composite bearing of the present invention has less frictional loss that causes heat generation and wear with respect to a load having an axial component, and other power loss that extends the life of the bearing. The industrial effect is extremely remarkable because it has a large effect of reducing the above-mentioned effect and has a wide range of applications.

[Brief description of drawings]

FIG. 1 is a sectional view parallel to a rotation axis showing a structure of an example of a first embodiment of the present invention.

FIG. 2 is a sectional view parallel to a rotation axis showing a structure of an example of a second embodiment of the present invention.

[Explanation of symbols]

1 Tapered cylindrical outer surface 2 inner ring 3 Tapered cylindrical inner surface 4 outer ring 5 taper roller 6 balls 7 circumferential groove 8 circumferential groove 9 disks 10 discs 11 Large diameter end face 12, 32 Axial end face 13 color members 14 rotation axis 15 cage 29 disks 30 sliding ring 33 Other axial end faces

Claims (3)

[Claims] 1. A first bearing, which is a so-called tapered roller type, in which an inner ring having a tapered cylindrical outer surface, an outer ring having a tapered cylindrical inner surface, and a plurality of tapered rollers are combined, and a first bearing of the first bearing. A composite rolling contacting a large-diameter side end surface of the taper roller, providing a disk rotatable concentrically with the first bearing, and disposing a bearing member for preventing axial movement of the disk. bearing. 2. A first bearing, which is a so-called tapered roller type, formed by combining an inner ring having a tapered cylindrical outer surface, an outer ring having a tapered cylindrical inner surface, and a plurality of tapered rollers, and a concentric bearing. A plurality of balls arranged on the circumference and a second bearing which is a so-called thrust ball bearing configured so as to be sandwiched by discs having circumferential grooves from both sides in the axial direction with the circle sandwiched therebetween; A composite rolling bearing, wherein the large diameter side end surface of the taper roller of the first bearing is arranged so as to abut against an axial end surface of one disk of the second bearing. 3. A first bearing, which is a so-called taper roller type, formed by combining an inner ring having a tapered cylindrical outer surface, an outer ring having a tapered cylindrical inner surface, and a plurality of taper rollers, and a concentric bearing. A second bearing which is a so-called sliding type thrust bearing in which a ring-shaped disc arranged on the circumference is rotatably provided, and the end surface on the large diameter side of the taper roller of the first bearing is A composite rolling bearing characterized in that it is arranged so as to come into contact with the axial end surface of one disk of the second bearing.