JPH0443627Y2 - - Google Patents

Description

[Detailed description of the invention] [Industrial application field] This invention relates to a double-row tapered roller bearing.

[Conventional technology]

As shown in Fig. 5, the double-row tapered roller bearing has an outer ring 1 and two inner rings 1 arranged inside the outer ring 1.
0, and on the inner circumferential surface of the outer ring 1, conical raceway surfaces 2 are formed in double rows, and a seal support surface for attaching a seal is continuous to the large diameter end of each raceway surface 2. 3',
3' is provided.

Further, on the outer circumferential surface of the inner ring 10, a conical raceway surface 11 is provided with respect to the raceway surface 2, a small pot 12 is formed at the small diameter end of the raceway surface 11, and a large pot is formed at the large diameter end. A pot 13 is provided, and the outer peripheral surface of the large pot 13 is used as a seal land 14.

mutually opposing raceway surfaces 2 of the outer ring 1 and the inner ring 10;
A tapered roller 20 is installed between 11 and 11. Further, a cylindrical portion 31 formed on the outer circumference of the seal core bar 30 is press-fitted into the seal support surface 3' of the outer ring 1, and a seal lip 32 formed on the inner circumference of the seal core bar 30 is press-fitted.
is pressed against the seal land 14 of the inner ring 10 to seal between the two rings 1 and 10.

When a double-row tapered roller bearing having the above configuration is used to support, for example, a hub (shaft) that is a component of a front wheel drive mechanism of an automobile, there is a double-row tapered roller bearing between the axle box 40 and the hub 41 inserted inside the axle box 40. The row tapered roller bearing A is press-fitted to prevent it from coming off.
To prevent this from coming off, a pair of fitting grooves 42, 42 are provided on the inner peripheral surface of the axle box 40, and a retaining ring 43 fitted in the fitting groove 42 is engaged with both end surfaces of the outer ring 1. Although not shown in the illustration, there is a shaft case 4.
There is one in which the bearing A is prevented from slipping off in one direction by a shoulder formed on the inner circumferential surface of the bearing A, and a retaining ring is used to prevent the bearing A from slipping off in the other direction in the same manner as described above.

Generally, in a front wheel drive mechanism of an automobile, in order to replace damaged parts or perform maintenance and inspection, the hub 41, which is fitted to the inner ring 10 with a seam opening, is often pulled out in the axial direction. in this case,
When the inner ring 10 fitted to the hub 41 with a seam opening is pulled out, the seal is damaged.
Since the tapered rollers 20 disassemble, it becomes necessary to replace them with new ones even if the double-row tapered roller bearing A is in a usable condition. Therefore, when removing the hub 41, it is necessary to prevent the inner ring 10 from remaining on the hub 41.

In order to prevent the inner ring 10 from being pulled out, as shown in FIG. Conventionally, there has been known a device in which the inner ring 10 is prevented from coming off by engagement with the small flange 12 of the inner ring 10.

[The problem that the idea attempts to solve]

As described above, if the inner ring 10 is prevented from being pulled out by the cylindrical portion 31 of the seal core 30 and the retaining ring 43 that pulls it up, an extremely large axial force is applied to the seal core 30. , the seal core metal 30 is easily deformed, and a large pull-out strength cannot be obtained. Even if the seal core metal 30 is made thicker and heat treated such as tuff try treatment in order to improve the strength, a significant improvement in strength cannot be expected, and fretting (seizing) may occur between the hub 41 and the inner ring 10. If the inner ring 10 is pulled out together with the hub 41, there will be an inconvenience.

In the tapered roller bearing disclosed in Japanese Utility Model Publication No. 55-9718, an auxiliary ring is fixed to the end face of the outer ring, and the large end face of the tapered roller bearing is engaged with the auxiliary ring to establish contact between the cage and the seal. However, since the inner diameter of the auxiliary ring is smaller than the diameter of the circumscribed circle of the large end face of the tapered rollers, after the inner ring and tapered rollers are assembled inside the outer ring, the auxiliary ring is attached by means such as welding. The problem is that the bearing must be installed by a screwdriver, which requires time and effort to assemble the bearing.

In addition, when fixing the auxiliary ring, if there is misalignment between the auxiliary ring and the outer ring, a step will occur at the joint between the two parts, making it impossible to assemble the tapered roller bearing. On the other hand, it is necessary to mount the auxiliary ring with high precision to avoid misalignment, and it takes time and effort to fix the auxiliary ring, and there are disadvantages in that the outer diameter of the auxiliary ring requires extremely high processing precision.

Therefore, the technical object of this invention is to solve the above-mentioned disadvantages, improve the pull-out strength of the inner ring of a double-row tapered roller bearing, and facilitate the assembly and processing of the bearing.

[Means to solve the problem]

In order to solve the above problems, in this invention, the outer circumference of the large end surface of the tapered roller 20 is engaged with the large diameter end of the conical raceway surface 2 formed in double rows on the inner circumferential surface of the outer ring 1. A cylindrical inner surface 3 is formed on the outside from the engaging groove 4, and the inner diameter of the cylindrical inner surface 3 is circumscribed by the large end surface of the tapered roller. We adopted a configuration with a diameter slightly larger than the circular diameter.

[Effect]

If the inner ring 10 moves in the axial direction with respect to the outer ring 1 and a gap is created between the raceway surfaces 2 and 11 of the inner and outer rings 1 and 10, all The tapered rollers 20 of the tapered rollers 20 are opened in the shape of a flap and are inclined in the outer diameter direction, and the outer circumferential portion of the large end surface engages with the engagement groove 4, and the small rib 12 of the inner ring
engages with the small end face of the tapered roller 20 and further rotates the tapered roller 20 in the outer radial direction, resulting in a locked state and the inner ring 10 and the tapered roller 20
is prevented from falling out.

On the other hand, when the shaft center of the bearing is horizontal, the tapered rollers in the lower half of the bearing are tilted in the same manner as described above, which prevents the inner ring from slipping out.

〔Example〕

Hereinafter, embodiments of this invention will be explained based on FIGS. 1 and 2. In addition, in the figure, the same parts as in the conventional example shown in FIG. 5 mentioned earlier are given the same reference numerals.
The explanation will be omitted.

As shown in the figure, the large diameter end of the conical raceway surface 2 formed in double rows on the inner circumferential surface of the outer ring 1 has an engagement groove in which the outer circumferential portion of the large end surface 21 of the tapered roller 20 can engage. 4 is provided at a required distance from the large end surface 21, and a cylindrical inner surface 3 is formed outward from the engagement groove 4.

The inner diameter D of the cylindrical inner surface 3 is approximately the same diameter as the circumscribed circle diameter d of the large end surface of the tapered roller 20, and the cylindrical portion 31 of the seal core bar 30 is press-fitted into the inner surface of the cylindrical inner surface 3.

1 and 2 show an example in which a hub 41 is rotatably supported, similar to the usage example of a conventional double-row tapered roller bearing. The outer ring 1 of the bearing fitted inside the four axle boxes is prevented from coming off by a shoulder 44 formed on the inner circumferential surface of the axle box 40 and a retaining ring 43 attached to the inner circumferential surface. .

Now, when the hub 41 is pulled out in the direction of the arrow in FIG.
0, the inner ring 10 located in the pulling direction moves together with the hub 41, and the raceway surfaces 2, 1 of the inner and outer rings move.
A gap is formed between the tapered rollers 1 and the tapered rollers 20, the tapered rollers 20 located in the lower half of the bearing are inclined in the outer diameter direction, and the outer periphery of the large end surface of the tapered rollers 20 fits into the engagement groove 4.

When the inner ring 10 moves further, the small ribs 12 come into contact with the small end surfaces of the tapered rollers 20 and push the tapered rollers 20, so that the outer periphery of the large end surface 21 of the tapered rollers 20 that has moved in the outer radial direction is As shown in FIG.
2, the tapered rollers 20 are further tilted in the outer radial direction around the engagement position with the engagement grooves 4 and are in a locked state, causing the tapered rollers 20 to engage with the engagement grooves 4.
The inner ring 10 is prevented from coming off through the inner ring 10.

In addition, in the example, the shaft center of the bearing is used horizontally, but when the shaft center is vertically used, the inner ring 1
Due to the axial movement of the tapered rollers 20, all of the tapered rollers 20 are opened in the shape of a flap and tilted in the outer diameter direction, and the outer circumferential portion of the large end surface of each tapered roller 20 engages with the engagement groove 4. Therefore, an extremely large pull-out strength can be obtained.

[Effect of idea]

As described above, according to this invention, the outer periphery of the large end surface of the tapered roller is engaged with the engagement groove formed on the inner periphery of the outer ring to prevent the inner ring from coming off, resulting in extremely high pull-out strength. Obtainable.

In addition, the cylindrical inner surface formed on the outside of the engagement groove is
Since the diameter is slightly larger than the circumscribed circle of the large end surface of the tapered rollers, the inner ring and tapered rollers can be assembled from the side of the outer ring, making it easy to assemble the bearing.

Furthermore, since it has a simple structure in which an engagement groove and a cylindrical inner surface are formed on the outer ring, it is easy to process.

[Brief explanation of the drawing]

Fig. 1 is a sectional view showing the sealed double-row tapered roller bearing according to the invention in use, Fig. 2 is an enlarged sectional view of the same bearing, and Fig. 3 is a sectional view showing another embodiment of the same bearing. Figure 4 is a cross-sectional view showing the state in which the inner ring in Figure 2 is prevented from coming off, Figure 5 is a cross-sectional view of a conventional sealed double-row tapered roller bearing, and Figure 6 is a state in which the inner ring is prevented from falling out in Figure 5. FIG. 1... Outer ring, 2... Raceway surface, 3... Cylinder inner surface,
4...Engagement groove, 10...Inner ring, 12...Small collar,
13...large brim, 20...conical corner, 21...
Large end face.

Claims (1)

[Scope of utility model registration request] An outer ring 1 and two inner rings 10 placed inside it
A plurality of tapered rollers 20 are installed in a double row between
The large diameter end of the inner ring 10 has a large collar 1 for guiding rollers.
3, and a small flange 1 at the small diameter end to prevent the roller from coming off.
In the double-row tapered roller bearing 2, the outer periphery of the large end surface of the tapered roller 20 can engage with the large diameter end of the conical raceway surface 2 formed in double rows on the inner peripheral surface of the outer ring 1. A cylindrical inner surface 3 is formed on the outside from the engaging groove 4, and the inner diameter of the cylindrical inner surface 3 is set to the diameter of the circumscribed circle of the tapered roller large end surface. A double-row tapered roller bearing characterized by a slightly larger diameter.