JP3039638B2 - Tapered roller bearing - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION A tapered roller bearing according to the present invention is mounted on a gear box of an automobile to rotatably support a shaft, or mounted on a suspension system of an automobile.
Used when the axle is rotatably supported.

[0002]

2. Description of the Related Art Tapered roller bearings incorporating trapezoidal tapered rollers are capable of supporting radial loads and axial loads, and have a large withstand load. ing. As shown in FIG. 2, such a tapered roller bearing has an outer ring 2 having a tapered inner race 1 and a tapered outer race 3.
An inner race 6 having a small flange 4 at a small-diameter end of the outer race 3 and a large flange 5 at a large-diameter end thereof, and a retainer 7 for connecting the inner race 1 and the outer race 3 to each other. And a plurality of tapered rollers 8, 8 held and guided between them.

[0003] Such a tapered roller bearing 9 is, for example, shown in FIG.
As shown in the figure, the outer race 2 is fitted inside the housing 10 and the inner race 6
Is fitted between the inner peripheral surface of the housing 10 and the outer peripheral surface of the shaft 11. When a radial or axial load is applied to the shaft 11 with the tapered roller bearing 9 mounted as described above, the load in any direction is supported by the tapered rollers 8 and 8, and the shaft 11 and the housing 10 are connected to each other. Relative rotation is smoothly performed.

[0004]

However, the tapered roller bearing constructed and used as described above has the following disadvantages. That is, the tapered roller bearing 9
As shown in FIG. 4, first, the plurality of tapered rollers 8, 8 held by the retainer 7 are combined with the inner ring 6, and then the plurality of tapered rollers 8, 8 are connected to the outer ring 2 as shown in FIG.
It is made to be assembled inside.

When a plurality of tapered rollers 8, 8 held by a retainer 7 are combined with the inner ring 6, both members 8, 6 are combined with the small flange portion 4 being on the lower side.
At this time, the plurality of tapered rollers 8, 8
(Rectangular through holes formed in the holder 7 in order to hold one tapered roller 8 in a freely rolling manner). The plurality of tapered rollers 8, 8 are not aligned in a normal state, and the relationship between the plurality of tapered rollers 8, 8 and the inner ring 6 is such that the tail-side (small-diameter side) end face of each of the tapered rollers 8, 8 is an inner ring. 6, the gap 12 exists between the head-side (large-diameter side) end face of each of the tapered rollers 8, 8 and the large flange 5 of the inner ring 6. In this state, when a plurality of tapered rollers 8, 8 are assembled inside the outer ring 2, as shown in FIG. 5, the gap between the head-side end face of each tapered roller 8, 8 and the large flange 5 of the inner ring 6 is increased. Is assembled in a state where the gap 12 remains.

In the use state of the tapered roller bearing 9,
As shown in FIG. 3, the head-side end faces of the tapered rollers 8, 8 come into contact with the large flange portion 5 of the inner ring 6, so that the head-side end faces of the tapered rollers 8, 8 are When the tapered roller bearing 9 assembled in a state where the gap 12 exists between the large collar portion 5 of the inner ring 6 and the housing 10 and the shaft 11 as shown in FIG. Accordingly, each tapered roller 8 moves toward the large collar portion 5 of the inner ring 6.

As described above, as the plurality of tapered rollers 8, 8 provided between the outer ring 2 and the inner ring 6 move toward the large flange 5, the respective tapered rollers 8, 8 and the outer ring 2 The pressure with which the inner raceway 1 comes into contact is reduced, and the preload of the tapered roller bearing 9 is insufficient. In order to prevent the occurrence of insufficient preload due to such causes, conventionally, the tapered roller bearing 9 is temporarily assembled between the housing 10 and the shaft 11 or the like, and then the housing 10 and the shaft 11 are relatively rotated. As a result, the tapered roller bearing 9 performs a familiar operation, and the head-side end faces of the plurality of tapered rollers 8 constituting the tapered roller bearing 9 are brought into contact with the large flange portion 5 of the inner ring 6, and then the tapered roller bearing 9. Is mounted (provided with a preload) between the housing 10 and the shaft 11 or the like.

However, in the case of the conventional tapered roller bearing 9, when the inner ring 6 and a plurality of tapered rollers 8, 8 are combined as shown in FIG. 4, the head-side end face of each of the tapered rollers 8, 8 and the inner ring Since the size of the gap 12 formed between the large flange 5 and the large flange portion 6 is large, the above-described familiar operation can be sufficiently performed (the housing 1).
The relative rotation between 0 and axis 11)
It was troublesome.

[0009] In view of such circumstances, Japanese Utility Model Publication No. 58-50
No. 094 discloses a structure in which a retainer is made of a synthetic resin having elasticity, and a part of the retainer is pressed against a small flange to press a tapered roller head side end face against a large flange. Are listed. According to such a structure, it is possible to prevent the occurrence of insufficient preload even if the familiar operation is reduced. However, in the case of the structure described in this publication,
The use of a special retainer not only increases the cost because there is no versatility of parts, but also increases the rotational torque because a part of the retainer and the small flange remain frictionally engaged. It is considered that heat generation during operation is likely to increase and failures such as burn-in are likely to occur. Further, the cage is easily broken, and there are many problems in terms of durability and reliability.

Further, in the case of the invention described in the above-mentioned publication, since a cage made of synthetic resin, which is inferior to metal in heat resistance and chemical resistance, is used, it cannot be used at high temperatures. It is unavoidable that the use is limited, for example, the type of lubricant that can be used is also limited. In addition, even if it can be used lubricant,
It is conceivable that abrasion powder generated by abrasion of the retainer contaminates the lubricant, which also causes a problem in terms of durability and reliability. Furthermore, since the synthetic resin retainer that always keeps rubbing against the inner ring wears out, it is necessary to replace the retainer when reassembling after disassembly for maintenance and inspection. Costs for maintenance and inspection increase. Furthermore, since it is necessary to make a part of the retainer made of synthetic resin project against the small flange portion on the outer peripheral surface of the inner ring, the width of the inner ring is
The size of the tapered roller bearing must be larger than necessary to construct the tapered roller bearing, and the size of the tapered roller bearing increases.
The present invention provides a tapered roller bearing capable of solving any of the above-mentioned disadvantages.

[0011]

A tapered roller bearing according to the present invention has an outer ring having a tapered inner race and a tapered outer race, and a small flange is provided at a small-diameter end of the outer race. Department
It is composed of an inner ring having a large flange formed at the large diameter end, and a plurality of tapered rollers which are held and guided between the inner and outer races by a retainer. In particular, in the tapered roller bearing of the present invention, when each of the tapered rollers is arranged at a regular position on the outer track of the inner ring, and when the tail side of each tapered roller is brought into contact with the small flange, The dimension ΔL of the gap formed between the head end surface of each tapered roller and the large flange.
Is set to 0.2 mm or less.

[0012]

The tapered roller bearing of the present invention constructed as described above is mounted between the housing and the shaft, so that the two members can rotate freely, and the radial load acting between the two members can be reduced. The operation itself in supporting the load in the axial direction is the same as that of the conventional tapered roller bearing described above.
In particular, in the case of the tapered roller bearing of the present invention, the dimension ΔL of the gap formed between the head-side end face of the tapered roller and the large flange portion is reduced, so that the tapered roller bearing is connected to the housing and the shaft. After assembling between the rollers, the running-in operation required for bringing the head side end surface of the roller into contact with the large flange portion is short, and the operation of applying a sufficient preload to the tapered roller bearing is facilitated.

When a cage is used, a general one is sufficient. In addition, in a state in which the preload is applied after the familiar operation is completed, the retainer functions in the same manner as a conventionally generally known tapered roller bearing, and the retainer does not rub against a part of the inner ring. Therefore, there is no increase in cost or increase in rotational torque or heat generation.
Therefore, the use of the tapered roller bearing is not limited based on the properties of the cage, and the reliability and durability can be easily secured. Also, it is not necessary to increase the width of the inner ring more than necessary to incorporate the cage.
Lightening is also easy.

[0014]

Next, the present invention will be described in more detail while describing experiments conducted for confirming the effects of the present invention.
The tapered roller bearing 9 of the present invention has an outer race 2 having a tapered inner race 1 and a tapered outer race 3 as shown in FIGS. Small collar 4 at the end
And an inner ring 6 having a large flange 5 formed at the large diameter end.
And a plurality of tapered rollers 8, 8 which are held and guided between the inner track 1 and the outer track 3 by a retainer 7.

The cage 7 is made of metal and is a cage-type cage in which windows 13, 13 smaller than the projected area of the tapered rollers 8, 8, are formed. 8 is larger than the pitch circle diameter. As a result, the plurality of tapered rollers 8, 8 held by the holder 7
Is mounted on the outer side of the inner ring 6, the plurality of tapered rollers 8, 8 are not separated from the inner ring 6, so that the two members 6, 8 can be integrally handled.

In the tapered roller bearing 9 of the present invention, as shown in FIG. 1, the tapered rollers 8 are arranged at regular positions on the outer raceway 3 of the inner ring 6, and the tail side of each tapered roller 8 and the small flange portion. 4, the dimension ΔL of the gap 12 formed between the head-side end face of each tapered roller 8 and the large flange portion 5 is regulated. That is, in the case of the present invention, the dimension ΔL of the gap 12 is set to 0.2 mm or less (ΔL ≦ 0.2 mm). On the other hand, in the case of the conventional tapered roller bearing, the dimension ΔL of the gap 12 is about 0.4 to 0.6 mm.

Next, as described above, the tapered rollers 8 are connected to the inner ring 6.
When the tail side of each tapered roller 8 and the small flange 4 are brought into contact with each other at a regular position on the outer orbit 3 of the tapered roller 3, the head side end face of each tapered roller 8 and the large flange 5 An experiment performed to confirm the effect when the dimension ΔL of the gap 12 formed therebetween is set to 0.2 mm or less will be described.

In the experiment, as shown in FIG. 5, the tapered roller bearing 9 assembled in such a manner that the head-side end faces of the tapered rollers 8, 8 do not come into contact with the large flange portion 5 of the inner ring 6 is mounted on the outer ring 2, By fixing the inner ring 6 as shown in the figure, the inner ring 6 was held horizontally, and the amount of displacement of the inner ring 6 due to the rotation of the inner ring 6 or the reciprocating swing was measured. That is, when the tapered roller bearing 9 assembled in the state as shown in FIG. 5 is operated, the inner ring 6 gradually descends with the movement of the inner ring 6, and the amount of the decrease is defined as the displacement amount of the inner ring 6. Measured and recorded. In the experiment, two products of the present invention having the gap 12 having a dimension ΔL of 0.13 mm and two conventional products having a dimension ΔL of the gap 12 of 0.55 to 0.60 mm were used.
And each was used.

First, in the first experiment, the inner ring 6 was rotated in one direction, and the amount of displacement of the inner ring 6 descending with the rotation was recorded in relation to the number of rotations. As a result, in the case of the product of the present invention, the displacement amount of the inner ring 6 changed as shown by broken lines a and b in FIG. 6 in relation to the number of rotations, whereas in the case of the conventional product, the solid lines c and d in FIG. It changed as shown by.

In the second experiment, the inner ring 6 was reciprocated by 30 degrees each time, and the amount of displacement of the inner ring 6 descending with the rocking was recorded in relation to the number of times of rocking. As a result, in the case of the product of the present invention, the displacement amount of the inner ring 6 depends on the number of swings as shown in FIG.
In contrast, in the case of the conventional product, it changed as shown by the solid lines g and h in FIG.

As is apparent from FIGS. 6 and 7, in the case of the tapered roller bearing 9 of the present invention, the inner ring 6 accompanying the familiar operation is used.
Is small, and is in a stable state at an early stage (the end faces on the head side of the tapered rollers 8, 8 come into contact with the large flange 5 of the inner ring 6,
(The state in which the inner ring 6 is not further displaced).

Further, as a third experiment, a plurality of tapered roller bearings 9 each having a slightly different dimension ΔL of the gap 12 are used, and the familiar operation is performed to rotate the inner ring 6 until a stable state is reached. When the number of times of the operation was measured, a result as shown in FIG. 8 was obtained. As is clear from FIG.
When the dimension ΔL of the gap 12 is 0.2 mm or less,
The number of times of the familiar operation can be reduced similarly, but when the size ΔL of the gap 12 exceeds 0.2 mm (ΔL> 0.2
mm), the number of required familiar operations increases gradually.

[0023]

The tapered roller bearing of the present invention is constructed and operates as described above. However, the simple construction does not increase the manufacturing cost, and the running-in operation required for maintaining a sufficient preload is small. As a result, the assembling work of the machine incorporating the tapered roller bearing can be made more efficient. In addition, it is possible to realize a tapered roller bearing which has a small rotating torque and a small amount of heat generation, is inexpensive, can be used for all purposes, and can secure sufficient durability and reliability.

[Brief description of the drawings]

FIG. 1 is a partial sectional view for explaining a tapered roller bearing of the present invention.

FIG. 2 is a partially cut perspective view of a tapered roller bearing to which the present invention is applied.

FIG. 3 is a sectional view showing an example of a usage state of the tapered roller bearing.

FIG. 4 is a sectional view showing a state in which the tapered roller bearing is assembled in an initial state of a process.

FIG. 5 is a sectional view showing the terminal device in the final state.

FIG. 6 is a diagram showing the results of a first experiment performed to confirm the effects of the present invention.

FIG. 7 is a diagram showing the results of the second experiment.

FIG. 8 is a diagram showing the results of the third experiment. DESCRIPTION OF SYMBOLS 1 Inner raceway 2 Outer race 3 Outer raceway 4 Small flange 5 Large flange 6 Inner ring 7 Cage 8 Tapered roller 9 Tapered roller bearing 10 Housing 11 Shaft 12 Clearance 13 Window

──────────────────────────────────────────────────続 き Continuation of the front page (56) References Jikken Sho 58-50094 (JP, Y2) Japanese Patent Publication No. 46-25202 (JP, B1) (58) Fields investigated (Int. Cl. ⁷ , DB name) F16C 19/36 F16C 33/46 F16C 33/58

Claims (2)

(57) [Claims] 1. An outer race having a tapered inner race, a tapered outer race, a small flange portion at a small-diameter side end of the outer race, and a large flange portion at a large-diameter side end. In the tapered roller bearing consisting of an inner ring each formed and a plurality of tapered rollers held and guided between the inner race and the outer race by a retainer, the tapered rollers are arranged on the outer race of the inner race. Arranged at the regular position, and when the tail side of each tapered roller and the small flange contact, the dimension ΔL of the gap formed between the head side end surface of each tapered roller and the large flange, Tapered roller bearings characterized by 0.2 mm or less. 2. A cage-shaped cage, wherein the cage is made of metal and has a window smaller than a projected area of each tapered roller, and the cage has a diameter larger than a pitch circle diameter of each tapered roller.
The tapered roller bearing according to claim 1.