JP2001221241A - Bearing device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To prevent deformation of an inner ring to eliminate influence of caulking upon bearing precision by increasing rigidity of the inner ring. SOLUTION: In this bearing device, a bearing 2 is installed to the periphery of a hub wheel 1 having a caulking cylindrical part 3a at a shaft end, the cylindrical part 3a is radially bent outward and is caulked to an end face of an opposite counter bore side end part 21a of the bearing inner ring 21. Thereby, the bearing 2 is prevented from coming off and is applied with pressure. Compared with a standard specification article, an opposite counter bore side shoulder part 21b of the inner ring 21 is radially bulged outward in a non-contact state with balls 23, and a radial thickness of the opposite counter bore side end part 21a is enlarged.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a bearing device such as a hub unit for a vehicle mounted on a vehicle such as an automobile.

[0002]

2. Description of the Related Art FIG. 8 shows an example of the structure of a vehicle hub unit as a conventional bearing device of this type.

The illustrated vehicle hub unit B has a hub wheel 1 and a double row outwardly directed angular ball bearing 2. The hub wheel 1 has an annular plate portion 11 and a shaft portion 12. A wheel (not shown) is attached to the annular plate portion 11.

The shaft end of the shaft portion 12 has a structure of a caulking portion 3 formed by rolling caulking. The angular ball bearing 2 is fixed to the outer periphery of the shaft portion 12.

The angular ball bearing 2 includes an inner ring 21 and an outer ring 2.
2, having a plurality of balls 23 and two crown-shaped retainers 24,
By the inner ring 21 being pressed from the caulked portion 3, a required preload (compressive stress) is applied and the inner ring 21 is prevented from coming off.

The retaining and preloading of the angular ball bearing 2 are performed instead of tightening the shaft end of the shaft portion 12 with a nut so far in order to reduce the weight by reducing the number of parts and the weight. It has become.

Here, the caulking cylindrical portion 3a indicated by a virtual line in the figure is constituted by the shaft end of the shaft portion 12, and is bent radially outward by the rolling of the caulking device 90. Then, it is caulked to the end face of the inner ring 21 of the angular ball bearing 2 to form the caulked portion 3.

[0008] As the above-mentioned caulking mode, a rolling caulking device C as shown in FIG. 9 is used. That is, the caulking cylindrical portion 3 at the shaft end of the shaft portion 12 of the hub wheel.
The caulking tool 90 is tilted at a required angle θ with respect to a, and the caulking tool 90 is rolled by rotating the rotating shaft 91 to plastically deform the caulking cylindrical portion 3a radially outward. The plastically deformed portion is pressed against the outer end surface of the inner race 21 as a caulking portion 3.

[0009]

In the case of the hub unit B, since the caulking force is applied to the inner ring 21 during the caulking, the orbit of the inner ring 21 is deformed into an irregular shape, and the roundness tends to decrease. As a result, not only the bearing accuracy is reduced, but also a circumferential tensile stress is applied to the track of the inner ring 21, which has an unfavorable effect on the fatigue life of the angular ball bearing 2.

Therefore, the applicant of the present application has thought that the thickness of the entire inner ring should be set large so as to increase the rigidity so that the inner ring is hardly deformed in swaging.

As described above, when increasing the thickness of the inner ring as a whole, the case where the inner diameter of the inner ring was reduced to increase the thickness was examined. It was found that the strength was reduced, and it was judged impossible to perform.

Therefore, an object of the present invention is to solve the problem of increasing the rigidity of the inner ring so that the inner ring is less likely to be deformed so that the bearing accuracy is not affected by swaging.

Another object of the present invention is to increase the rigidity of the inner ring so that the inner ring is less likely to be deformed without reducing the strength of the shaft portion against caulking.

[0014]

In a bearing device according to the present invention, an oblique contact type rolling bearing is mounted on the outer periphery of a shaft having a caulking cylindrical portion at a shaft end, and the caulking cylindrical portion of the shaft is formed into a diameter. A bearing device that bends outward in the direction and crimps against the end face of the inner ring of the rolling bearing on the side opposite to the counterbore to prevent the rolling bearing from slipping off and to apply a preload. The portion is bulged radially outward with respect to the standard specification product, and the radial thickness at the end opposite to the counter bore is increased.

According to the present invention, the shoulder of the inner ring opposite to the counter bore is bulged radially outward with respect to the standard specification product,
Since the radial thickness of the counter-bore-side end is increased, the volume of the counter-bore-side end is increased and the section modulus is increased, so that the rigidity of the counter-bore-side end is increased.

For example, when the caulking tool is rolled to bend the caulking cylindrical portion radially outward and crimped to the end face of the counter-bore-side end of the inner race, the caulking force is reduced by the counter-counter of the inner race. It covers the bore side end,
The end on the side opposite to the counter bore has high rigidity and is not deformed by swaging. Therefore, the raceway side portion of the inner race is not deformed by caulking, so that the roundness of the raceway is maintained, and the bearing accuracy is maintained.

Also, since the end portion on the side opposite to the counter bore is not caulked and deformed, the caulking does not apply a tensile stress in the circumferential direction to the raceway of the inner ring. As a result, bearing fatigue is reduced by caulking and the life is shortened. Is not shortened.

Further, according to the present invention, since the thickness of the entire inner ring is not set to be large, it is not necessary to reduce the inner diameter of the inner ring, so that it is not necessary to reduce the shaft diameter of the shaft, and the shaft strength is reduced. In the held state, it can be swaged without deforming the inner ring.

In a preferred embodiment of the present invention, the outer diameter of the counter bore side end is larger than the rolling element pitch circle diameter and smaller than the inner diameter of the outer ring counter bore. In this case, the rigidity of the counter bore side end can be improved without lowering the rolling performance of the rolling element.

Further, in a preferred embodiment of the present invention, the bulging portion at the end opposite to the counter bore is set so as not to contact the rolling element. In this case, the rigidity of the counter-bore-side end can be improved without lowering the rolling performance of the rolling element.

In a preferred embodiment of the present invention, a rotation detecting device is further provided, the rotation detecting device comprising: a pulsar ring provided on an axially outer end face of the bulging portion; And an electromagnetic sensor provided at a non-rotating portion facing the above. In this case, even if the centrifugal force associated with the rotation of the inner ring acts on the pulsaring, the pulsaring does not change the distance between the pulsaring and the electromagnetic sensor at all, so that a rotation detecting device with high rotation detection accuracy can be obtained.

In this case, the pulsar ring is provided on the axially outer end face of the bulging portion even if the radial gap between the counterbore end of the inner ring and the counterbore of the outer ring is reduced by the bulging portion. Therefore, it is possible to easily obtain an installation space for the rotation detecting device and obtain a rotation detecting device having high rotation detecting accuracy while improving the rigidity of the counter-bore side end without lowering the rolling performance of the rolling element. Is obtained.

[0023]

DESCRIPTION OF THE PREFERRED EMBODIMENTS The details of the present invention will be described below based on embodiments shown in the drawings.

(Embodiment 1) FIGS. 1 to 3 show a vehicle hub unit which is an example of a bearing device according to Embodiment 1 of the present invention. FIG. 1 shows a state before caulking by a caulking cylindrical portion 3a. FIG. 2 is a longitudinal sectional side view of the hub unit in a state, FIG. 2 is a longitudinal sectional side view of the hub unit in a state after caulking by the caulking cylindrical portion 3a, and FIG.
3 is an enlarged view of a main part of FIG.

In the figures, A denotes the entire vehicle hub unit as a bearing device, 1 denotes a hub wheel as a shaft, 2 denotes a double row outward angular ball bearing as a rolling bearing, and 3a denotes a hub wheel. A caulking cylindrical portion provided at one shaft end. The caulking cylindrical portion 3a shown in FIG.
Is bent outward in the radial direction to form the caulked portion 3 shown in FIG.

The hub wheel 1 has an annular plate portion 11 and a shaft portion 12 on which a double-row outward-facing angular ball bearing 2 as an example of an oblique contact type rolling bearing is mounted. Note that the present invention is not limited to the angular contact ball bearing 2 as the oblique contact type rolling bearing.
Anything is fine. For example, rolling bearings such as counterbore ball bearings, single-row angular contact ball bearings, and double-row tapered roller bearings are included.

The angular ball bearings 2 are arranged in two rows: an inner race 21 having a single race fitted to the small diameter outer peripheral surface of the shaft portion 12, a single outer race 22 having two rows of race grooves. A plurality of balls 23 as rolling elements and two crown-shaped cages 24 are provided, and the large-diameter outer peripheral surface of the shaft portion 12 of the hub wheel 1 is formed as one inner ring. The inner ring 21 uses the inner ring of a general single-row angular contact ball bearing as it is. A radially outward flange 25 is provided on the outer periphery of the outer ring 22.
5 and non-rotatably attached to an axle case (not shown).

In FIG. 2, reference numeral 30 denotes a lid.

The above-described vehicle hub unit A is basically a hub wheel 1 having a caulking cylindrical portion 3a at the shaft end.
An angular contact ball bearing 2 is mounted on the outer periphery of the cylindrical ball bearing, and the caulking cylindrical portion 3a is bent radially outward so as to be caulked on the end face of the counter ring side end 21a of the inner ring 21 of the angular contact ball bearing 2. 2 and a preload is applied.

The structure of the first embodiment is as follows.
An anti-counter bore side shoulder 21b of the inner ring 21 is bulged radially outward with respect to the standard specification product in a non-contact state with the ball 23, and the bulged portion 21c of the anti-counter bore side end 21a is formed. That is, the radial thickness is increased.

The configuration further characterized in the first embodiment is further characterized in that the outer diameter D0 of the counter-bore-side end portion 21a whose radial thickness is increased as described above is preferably the pitch of the balls 23. It is larger than the circular diameter (PCD) D1 and smaller than the inner diameter D2 of the counter bore 22a of the outer race 22.

Here, the standard specification product is defined as one having a shoulder height of the inner ring of not less than the minimum height required for preventing the rolling element from running over and not more than the pitch circle diameter of the rolling element.

In the vehicle hub unit A having the above-described structure, the radially thick portion of the counter-bore-side end portion 21a is enlarged by the bulging portion 22a, so that its rigidity is increased.

Accordingly, when the caulking device is rolled to bend the caulking cylindrical portion 3a of FIG. 1 radially outward and crimped to the end face of the counterbore-side end portion 21a of the inner race 21, the caulking force is generated. Even if it is applied to the counter-bore-side end 21a of the inner race 21, the counter-bore-side end 21a has a high rigidity as described above, and is not deformed by swaging.

The outer diameter of the counter bore side end 21a is D0, and the pitch circle diameter P. C. D. Is D1 and the inner diameter of the counter bore 22a of the outer race 22 is D2, the magnitude relationship is D1 ≦ D0 ≦ D2. However, in the case of increasing the rigidity of the counter bore side end, a more preferable range is 0.15. ≦ (D0−D1) / (D2−D1) ≦ 0.75.

The material of the inner ring 21 is preferably high carbon chromium bearing steel according to JIS standards, but the material is not limited to this.

Therefore, the caulking does not affect the portion of the inner ring 21 on the track side, and the track is not deformed by caulking, so that the roundness of the track is maintained and the bearing accuracy is maintained.

Further, since the counter-bore-side end 21a is not deformed by caulking, a circumferential tensile stress is not applied to the race of the inner ring 21 by caulking. As a result, bearing fatigue is reduced by caulking. Life is not shortened.

Further, since the thickness of the entire inner ring 21 is not set to be large, it is not necessary to reduce the inner diameter of the inner ring 21, that is, it is not necessary to reduce the shaft diameter of the hub wheel 1. In this state, the inner ring 21 can be swaged without being deformed.

The first embodiment described above is not limited to a vehicle hub unit comprising a combination of a hub wheel 1 and an angular ball bearing 2, but includes a hub wheel or the like as a shaft and an angular ball bearing or the like. It can also be applied to a bearing device in which the oblique contact type rolling bearing is disposed on the outer periphery of the shaft portion of the shaft body.

(Embodiment 2) FIGS. 4 to 6 relate to Embodiment 2 of the present invention. FIG. 4 is a longitudinal sectional side view of a bearing device according to Embodiment 2, and FIG. FIG. 6 is a partially exploded perspective view of the detection device, and FIG. 6 is an enlarged view of a main part of the bearing device shown in FIG. FIG. 7 is an enlarged view of a main part of a conventional bearing device for comparison with the second embodiment.

4 to 6, parts corresponding to those in FIGS. 1 to 3 are denoted by the same reference numerals, and the description of the parts corresponding to the same reference numerals is omitted.

The feature of the second embodiment is that a rotation detecting device 40 for detecting the rotation speed of the wheels is provided.

That is, the rotation detecting device 40 provided in the bearing device of the second embodiment is, for example, an information input means in an ABS (anti-lock brake system) of an automobile, and other components.
It is used when data on the rotation state of wheels is required.

The rotation detecting device 40 includes a pulsaring 4
1, an electromagnetic sensor 42, and a control unit 43.

The pulsar ring 41 is an annular bulging portion 21 provided at the counter-bore-side end 21a of the inner ring 21 of the angular ball bearing 2 which is a rotating portion of the bearing device A.
c is attached to the axially outer end face.

The electromagnetic sensor 42 is attached to the cover 30 which is a non-rotating part of the bearing device A.

The control unit 43 is attached to the electromagnetic sensor 42 via wiring and includes a microcomputer and the like, and calculates the rotation speed of the wheels and the like from the output signal of the electromagnetic sensor 42 and performs various controls. I have.

In the bearing device A of the second embodiment, the wheels (not shown) are attached to the outer surface of the annular plate portion 11 of the hub wheel 1, so that the rotation speed of the wheels corresponds to the rotation speed of the pulsar ring 41. Therefore, the magnetic change of the pulsar ring 41 corresponds to the rotation speed of the wheel.

More specifically, as shown in FIG. 5, the pulsar ring 41 is formed of a ring body having a magnetic pole forming surface in which N magnetic poles and S magnetic poles are alternately arranged in the circumferential direction. The sensor 42 has a pulsaring 41
So that an electromagnetic signal having a frequency corresponding to an alternating close cycle of each of the N and S magnetic poles of the pulsar ring 41 can be output to the control unit 43. Has become.

The control unit 43 calculates data such as the rotational speed of the wheels from the frequency of the electromagnetic signal.

The rotation detecting device 40 according to the second embodiment and the conventional rotation detecting device 40a will be described with reference to FIGS. 6 and 7. FIG. FIG. 6 illustrates a rotation detection device 40 according to the second embodiment.
FIG. 7 shows a conventional rotation detecting device 40a.

In the case of the rotation detecting device 40 according to the second embodiment, the main part of which is shown in FIG.
The counter-bore-side end 21a is radially bulged by the bulging portion 21c, so that the axially outer end surface of the bulging portion 21c provides a wide installation space for the pulsar ring 41. Therefore, the pulsar ring 41 can be installed on the axially outer end face of the bulging portion 21c, and the electromagnetic sensor 42 can be installed facing the pulsar ring 41 in the axial direction.

In the case of the rotation detecting device 40 of the second embodiment having the above configuration, even if the centrifugal force accompanying the rotation of the inner ring 22 acts on the pulsar ring 41, the magnetic pole forming surface of the pulsar ring 41 is displaced in the axial direction. Therefore, the distance between the electromagnetic sensor 42 and the sensor surface does not change at all. Therefore, the output of the electromagnetic sensor 42 from the pulsar ring 41 for detecting the alternate approaching period of each magnetic pole accurately corresponds to the rotation speed of the wheel, and the rotation detection accuracy can be high.

On the other hand, in the case of the conventional rotation detecting device 40a whose main part is shown in FIG. 7, the pulsar ring 41 is extended in the axial direction while the bulging portion 21c is not provided. The pulsar ring 41 and the electromagnetic sensor 42 are radially opposed to each other. Therefore, when a centrifugal force caused by the rotation of the inner ring 22 acts on the pulsar ring 41, the pulsar ring 41 bends inward and outward in the radial direction as shown by the phantom line, and the distance between the pulsar ring 41 and the electromagnetic sensor 42 must be kept constant. Becomes difficult. If the facing distance between the pulsar ring 41 and the electromagnetic sensor 42 changes as described above, the rotation cannot be detected with high accuracy.

The rotation detecting device 40 according to the second embodiment is
Pulser ring 4 to detect wheel rotation by magnetic change
1 and the electromagnetic sensor 42, but the invention is not limited to such a combination.

Further, the pulsaring 4 of the second embodiment described above.
Reference numeral 1 denotes a metal ring body in which N and S magnetic poles are alternately arranged in the circumferential direction on the magnetic pole forming surface, or a metal ring body in which a plurality of windows are formed in the circumferential direction at equal intervals or at a fixed rule. On the other hand, the electromagnetic sensor 42 is configured by a permanent magnet and configured to generate and output a signal corresponding to an electromagnetic change in the circumferential direction due to the rotation of the pulsar ring 41,
A signal in which the frequency of the electromagnetically responsive signal changes according to the rotation speed of the pulsar ring 41 may be output, and the signal may be input to the control unit 43, and the control unit 43 may detect the rotation speed from this signal. .

[0058]

As described above, in the bearing device of the present invention, the radial thickness of the end portion on the side opposite to the counterbore is enlarged.
The inner ring has an increased rigidity at the end opposite to the counter bore. Therefore, for example, when the caulking tool is rolled to bend the cylindrical portion for caulking radially outward and caulked to the end face of the counter bore side end of the inner ring, the caulking force is the counter counter bore end of the inner ring. However, since the rigidity of the counter-bore side end is large, it is not deformed by caulking, so that the raceway side portion of the inner ring is not deformed by caulking, and the roundness of the raceway is maintained, Bearing accuracy is maintained.

Further, since the end portion on the side opposite to the counter bore is not caulked and deformed, the caulking does not apply a tensile stress in the circumferential direction to the raceway of the inner ring. As a result, bearing fatigue is reduced by caulking and the life is reduced. Is not shortened.

Further, according to the present invention, since the thickness of the entire inner ring is not set to be large, it is not necessary to reduce the inner diameter of the inner ring. Therefore, it is not necessary to reduce the shaft diameter of the shaft. While maintaining the strength of the inner ring, the inner ring can be swaged without deforming the inner ring.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional side view of a vehicle hub unit according to a first embodiment of the present invention before swaging.

FIG. 2 is a longitudinal sectional side view of the vehicle hub unit according to the first embodiment of the present invention after swaging.

FIG. 3 is an enlarged view of a main part of the first embodiment shown in FIG. 1;

FIG. 4 is a longitudinal sectional side view of a vehicle hub unit according to a second embodiment of the present invention.

FIG. 5 is a partially exploded perspective view of a rotation detection device provided in the vehicle hub unit according to the second embodiment.

FIG. 6 is an enlarged view of a main part of the second embodiment.

FIG. 7 is an enlarged view of a main part of the related art corresponding to FIG.

FIG. 8 is a longitudinal sectional side view of a conventional vehicle hub unit.

9 is a process chart for explaining a caulking mode of a caulking portion in FIG. 8;

[Explanation of symbols]

 Reference Signs List A vehicle hub unit 1 hub wheel (shaft) 12 hub wheel shaft 2 double row outward angular ball bearing (rolling bearing) 3 caulking portion 3a caulking cylindrical portion 21 inner ring 21a counter-bore end of inner ring 21 21b Counter-bore-side shoulder 21c of inner ring 21 Protruding portion of counter-bore-side end 21a 22 Outer ring 22a Counterbore of outer ring 22 Ball (rolling element) 40 Rotation detecting device 41 Pulser ring 42 Electromagnetic sensor

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[Procedure amendment]

[Submission date] March 10, 2000 (200.3.1.1)
0)

[Procedure amendment 1]

[Document name to be amended] Statement

[Correction target item name] Claims

[Correction method] Change

[Correction contents]

[Claims]

──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. ⁷ Identification symbol FI theme coat ゛ (reference) F16C 25/08 F16C 25/08 Z F term (reference) 3D046 BB11 BB28 HH36 3J012 AB04 BB03 CB10 FB09 FB10 FB12 3J017 AA02 DA01 DB08 3J101 AA32 AA43 AA54 AA62 AA72 AA81 BA80 FA44 GA02

Claims (5)

[Claims] An oblique contact type rolling bearing is mounted on the outer periphery of a shaft body having a caulking cylindrical portion at a shaft end, and the caulking cylindrical portion of the shaft body is bent outward in a radial direction. Caulking the end face of the inner ring opposite the counter bore side,
A bearing device for retaining a rolling bearing and applying a preload, wherein a shoulder of a counter bore side of an inner ring is bulged radially outward with respect to a standard specification product, and a diameter of an end of the counter bore side is reduced. A bearing device having an increased thickness in a direction. 2. The bearing device according to claim 1, wherein an outer diameter of the counter bore side end is larger than a rolling element pitch circle diameter and smaller than an inner diameter of a counter bore of the outer race. 3. The bearing device according to claim 1, wherein a bulging portion at an end opposite to the counter bore is set so as not to contact the rolling element. 4. The bearing device according to claim 1, further comprising a rotation detecting device, wherein the rotation detecting device includes a pulsar ring provided on an axially outer end face of the bulging portion and a pulsar ring. And a magnetic sensor provided at a non-rotating portion axially facing the non-rotating portion. (5)