JPH0566327U - Parallel combination type double row angular contact ball bearing - Google Patents

Abstract

(57) [Abstract] [Purpose] To provide a parallel combination type double-row angular contact ball bearing with a large load capacity without variations in DT clearance and DT clearance. [Structure] Two rows of raceway grooves 5a, 5 on the outer peripheral surface of the integral inner ring 2
b is provided. In addition, two rows of raceway grooves 4a are formed on the outer ring 1
4b is provided. Many balls 3 between these raceways
a, 3b and cages 8a, 8b are incorporated. Further, the outer ring 1 is provided with the counter bore 6 only on one side surface side, and the inner ring 2 is provided with the shoulder recess portion 7 only on the end surface side opposite to the counter bore.

Description

[Detailed description of the device]

[0001]

[Industrial applications]

 The present invention relates to a double-row angular contact ball bearing used in a portion where a radial load and a relatively large axial load are applied, such as a final reduction gear of an automobile.

[0002]

[Prior Art]

 At locations where the axial load is large, two single-row angular contact ball bearings are used in combination in a DT type, that is, in parallel, depending on the normal load state. Such a combination is a well-known technology (for example, "NACHI rolling bearings"). Technical Handbook ”No. 30 02-8, page 5). Further, as shown in FIG. 4C, a double row deep groove ball bearing having a contact angle in the same direction between both rows is also used.

[0003]

[Problems to be solved by the device]

 However, when two single row angular contact ball bearings are used in combination, each bearing is manufactured as a single unit independently of each other, and when these are arbitrarily selected and combined, As shown in (a) and (b), a DT clearance wa may be left in the inner ring and a DT clearance wb may be left in the outer ring between the opposed end surfaces of the inner rings 2a and 2b and between the opposed end surfaces of the outer rings 1a and 1b. Many. Moreover, the outer and inner diameters of the juxtaposed bearings are often different, and the fitting allowances with the axle box and the shaft are often different. Therefore, the shrinkage of the outer ring and the inner ring due to the tightening allowance and the expansion amount are varied, which further promotes the variation in the DT clearance. Also, if there is a DT clearance, when one axial load is applied, only one bearing will receive an external force until this clearance is killed, so the bearing on the side receiving the external force will be damaged early, and the other bearing will have a ball. Will not roll normally and the rolling surface will be damaged, resulting in the problem that the bearing is likely to be damaged. In order to solve such a problem, a bearing maker preliminarily adjusts so as to eliminate the clearances wa, wb between opposed end faces of a pair of bearings as a bearing exclusively for combination, but it is necessary to perform processing for adjustment. Therefore, there was also the problem that the bearings would become expensive.

Further, the integrated double-row ball bearing shown in FIG. 4 (c) solves the above-mentioned problem of the combined type, but this integrated double-row ball bearing is a so-called conrad type. Therefore, since the balls 3a and 3b are incorporated, as many balls as the single-row angular contact ball bearing cannot be incorporated, and the load capacity cannot be increased.

[0005]

[Means for Solving the Problems]

 The parallel combination double-row angular contact ball bearing according to the present invention is provided with two rows of raceway grooves on the outer peripheral surface of the integral inner ring, and raceway grooves corresponding to the raceway grooves on the inner circumferential surface of the integral outer ring. In each of the two rows of raceway grooves, a large number of balls and a retainer that equally distributes the balls on the raceway grooves are provided, and only one end face side of the outer ring and the side end face side of the inner ring opposite to the side end are provided. The counterbore (in this specification, the counterbore is the inscribed circle diameter of the balls 3a, 3b when the balls are pressed against the groove bottoms of the outer raceway grooves 4a, 4b as shown in FIG. 5). A is the amount of interference δ between A and the counter bore diameter B of the inner ring. Note that the diameter difference between the raceway groove bottom C of the track ring and the above B is used as a counter bore for convenience. The amount of interference with the ball from either the counter bore or shoulder In addition, by making the counter bore and shoulder shoulder both have zero ball interference, it is possible to increase the number of balls to be incorporated, which increases the load capacity and also the DT clearance variation. In addition, the influence of the clearance due to the variation in the tightening margin is completely eliminated.

[0006]

[Action]

 The parallel combination type double row angular contact ball bearing according to the present invention can always receive a load evenly in both rows at a portion to which a large axial load is applied, so that it stably rotates even under a high load condition. Long life is guaranteed.

[0007]

【Example】

 Next, an embodiment of the present invention will be described with reference to the drawings. As shown in FIG. 1, two rows of raceway grooves 4a and 4b are provided on the inner peripheral surface of the outer ring 1, and raceway grooves 5a and 5b are formed on the outer peripheral surface of the inner ring 2 in correspondence with the raceway grooves 4a and 4b. It is set up. Further, a large number of balls 3a, 3b and cages 8a, 8b for equally distributing these balls are rotatably incorporated in the raceway grooves 4a, 4b and 5a, 5b. A counter bore 6 is provided on one end of the outer ring 1. On the other hand, the inner ring 2 is provided with a shoulder recess 7 at the end opposite to the counterbore 6.

Further, one of the counter bore 6 and the shoulder cushion 7 has no interference amount. In order to assemble the balls 3a and 3b in this bearing, as shown in FIG. 2, the ball 3a is previously locked by the retainer 8a on the track 4a having no counterbore of the outer ring 1 and the counterbore of the other inner ring having no counterbore. The ball 3b is previously locked to the track 5b by the retainer 8b. Next, the outer ring 1 is heated by an appropriate means, and the inner and outer rings are moved relative to each other in the direction of arrow A to complete the assembly. In this case, if either the counterbore 6 or the shoulder recess 7 has an amount of interference, the inner and outer rings will not separate when the outer ring 1 reaches room temperature after the assembly is completed.

Further, by using the method of simultaneously grinding both rows when forming the two rows of raceway grooves for the inner and outer rings, the DT clearance found in the combined bearing is eliminated. In addition, since the inner and outer rings are integrated, each row of balls has the same tightening margin, and each row evenly supports the load against the outer axial load. FIG. 3 shows a pinion shaft of a final reduction gear of an automobile incorporating a parallel combination type double-row angular contact ball bearing according to the present invention. In this case, both the counter bore 6 and the shoulder recess 7 have no interference amount, and the advantage of being able to obtain low torque by directly applying the assembly procedure of the conventional single row tapered roller bearing There is.

[0010]

【effect】

 In the parallel combination type double row angular contact ball bearing according to the present invention, two rows of raceway grooves 5a, 5b are provided on the outer peripheral surface of the integral inner ring 2 and the raceway groove is formed on the inner circumferential surface of the integral outer ring 1 as described above. Corresponding raceway grooves 4a, 4b are provided, and a large number of balls 3a, 3b and cages 8a, 8b for equally arranging these balls are provided in the two rows of raceway grooves, respectively. The counterbore 6 and the shoulder recessed portion 7 are formed only on the end surface side and the side end surface side of the inner ring opposite to the above side, and a double row angular contact ball bearing equivalent to a single DT combination angular contact ball bearing is configured. As a result, the variation in the DT clearance and the variation in the tightening allowance, which have been observed in the past, have no effect on the clearance variation. In addition, the bearing can be designed to be narrower in the axial direction than the combined bearing, which has the advantage of being light and compact. Furthermore, compared to the conventional double-row deep groove ball bearing, not only the number of balls is large, but also a cage that does not have a break can be used in the pocket portion, so there is no risk of the cage falling off. If the counterbore 6 and shoulder shoulder portion 7 have no interference, they can be assembled in the same manner as a tapered roller bearing, and the bearing according to the present invention is replaced with a tapered roller bearing. It became easier.

[Brief description of drawings]

FIG. 1 is a sectional view of an embodiment of the present invention.

FIG. 2 is a sectional view showing an assembled state of the present invention.

FIG. 3 is a sectional view of the bearing of the present invention applied to a final reduction gear pinion shaft for an automobile.

FIG. 4 is a cross-sectional view of a conventional product, (a) and (b) showing a combination of single-row angular contact ball bearings, and (c) showing a double-row deep groove bearing.

FIG. 5 is a cross-sectional view of a double-row bearing showing the amount of interference.

[Explanation of symbols]

 1 outer ring 2 inner ring 3 ball 4 raceway groove (outer ring) 5 raceway groove (inner ring) 6 counterbore 7 shoulder recess

Claims (3)

[Scope of utility model registration request] 1. A two-row raceway groove is provided on an outer peripheral surface of an integral inner ring, a raceway groove corresponding to the raceway groove is provided on an inner circumferential surface of an integral outer ring, and a plurality of raceway grooves are provided in each of the two rows. A ball and a cage that distributes the ball equally on the raceway groove are interposed, and a counterbore and a shoulder pad are provided only on the one end face side of the outer ring and the side end face side of the inner ring opposite to the side face end. A parallel combination type double row angular contact ball bearing, characterized in that the counterbore and shoulder shoulder both have an appropriate amount of interference with the balls. 2. The amount of interference between the counterbore and one of the shoulder cushions and the ball is set to zero.
Parallel combination type double-row angular contact ball bearing described. 3. The parallel combination type double-row angular contact ball bearing according to claim 1, wherein the counterbore and the shoulder cushion both have zero interference with the ball.