JP2003336650A - Ball bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a sufficient ball bearing obtaining a low torque, a low variation of torque and a high rotation accuracy by effectively depositing a grease deposited on a shoulder surface of a bearing ring onto a sea member side. <P>SOLUTION: In the ball bearing 10, a plurality of balls 14 rollable between an inner ring 12 and an outer ring 13 are circumferentially arranged at a predetermined space while they are retained in respective pockets of a crown type retainer 15. A seal member 16 is attached to both end openings in an axial direction. Inclination parts 16a, 16b provided with inner side surfaces inclined toward shoulder surfaces 12b, 13b of the corresponding respective inner and outer rings 12, 13 are formed on the respective inner and outer peripheral ends of the seal member 16 positioned at a pocket opening side of the crown type retainer 15. <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a ball bearing, and more particularly to an improvement of a ball bearing which is used in a rotary support portion of a small motor such as a fan motor for an air conditioner and which has a crown type cage.

[0002]

2. Description of the Related Art Conventionally, in a ball bearing used for a rotation supporting portion of a small motor such as an air conditioner fan motor, a lubricant such as grease is used in order to improve rocking resistance (fretting resistance) during transportation. Enclosed in the raceway groove of the bearing ring,
The enclosed amount is generally about 30% of the internal volume of the bearing.

In the ball bearing as described above, as shown in FIGS. 8 and 9, a plurality of balls 4 which are rollable between an inner ring 2 and an outer ring 3 fitted to a shaft 1 are crown type cages. It is held in each pocket of No. 5 and arranged at a predetermined interval in the circumferential direction. Sealing members 6A and 6B for preventing foreign substances from entering and preventing grease from leaking from the outside are attached to openings of both ends of each ball bearing in the axial direction.

Each of the seal members 6A and 6B is generally formed into a flat ring shape except for the caulking portion 7A and the fitting portion 7B for the outer ring 3. The seal member 6A shown in FIG. 8 is a press-molded iron shield, and the seal member 6B shown in FIG. 9 is an elastic seal in which resin or rubber is integrally molded around a core metal. These seal members 6A,
6B is a seal groove 3 formed at both ends of the inner peripheral surface of the outer ring 3.
It is crimped or fitted to s.

[0005]

By the way, when the ball bearing of this kind of structure is rotated by grease lubrication, for example, the grease enclosed in the raceway groove 3a of the outer ring 3 is not exposed to the pocket opening side of the crown type cage 5. In the above, the excess amount moves and adheres to the shoulder surface (track groove shoulder surface) 3b due to the application of the preload. Also,
The grease moves to the vicinity of the top of the rotation shaft of the ball 4 as the bearing rotates, and accumulates on the shoulder surfaces 2b and 3b of both the inner and outer races 2 and 3. Further, the grease that cannot be completely deposited on these portions will be deposited on the space between the claws (columns) of the crown type cage 5.

Thus, the shoulder surfaces 2b, 3 of the inner and outer rings 2, 3 are
When grease is accumulated in the area b of the crown type cage 5 or in the vicinity of the pocket portion of the crown type cage 5, the ball bearing may have a high torque or an intermittent torque fluctuation due to the sudden movement of the grease into the raceway grooves 2a and 3a and the pocket. However, there is a problem that the rotation accuracy is deteriorated as a result.

Therefore, for example, as shown in FIG.
By making the seal member 6 have a cross-sectional shape that extends straight from the shoulder surface of the seal groove 3s to the inner ring 2 side without a step, the grease G accumulated on the shoulder surface 3b of the outer ring 3 moves to the seal member 6 side. Then, it is possible to solve the above problems.

However, in this case, the grease G once attached to the seal member 6 side returns to the ball 4 side again due to the short distance between the seal member 6 and the ball 4, resulting in the grease G. May not be effectively attached to the seal member 6 side.

Therefore, an object of the present invention is to solve the above-mentioned problems. By effectively adhering the grease accumulated on the shoulder surface of the bearing ring to the seal member side, low torque,
An object of the present invention is to provide a good ball bearing capable of obtaining low torque fluctuation and high rotation accuracy.

[0010]

The above object of the present invention is to provide a plurality of balls, which are rollable between an inner ring and an outer ring, in respective pockets of a crown type cage and arranged at predetermined intervals in the circumferential direction. A ball bearing which is provided and has a seal member attached to both end openings in the axial direction, and which corresponds to at least each inner and outer peripheral end portion of the seal member located on the pocket opening side of the crown type cage. This is achieved by a ball bearing characterized in that an inclined portion having an inner side surface inclined toward the shoulder surface of each inner and outer ring is formed.

According to the above construction, the inclined portion having the inner side surface inclined toward the shoulder surface of each corresponding inner and outer ring is formed at each inner and outer peripheral end portion of the seal member on the pocket opening side of the crown type cage. To be done. Therefore, the grease accumulated on the shoulder surface of the bearing ring can be positively moved to the seal member side and adhered thereto.

Since the grease is secured in the space away from the balls and the sudden movement of the grease into the raceway grooves or pockets is prevented, balls with low torque, low torque fluctuation, and high rotation accuracy are provided. A bearing can be realized. or,
The base oil oozes out from the grease accumulated on the seal member side and enters the raceway groove along the inclination of the inclined part, so a stable supply of lubricating oil is possible and the rotation performance of the bearing is improved. Can be achieved.

Preferably, the radial cross section of the seal member is symmetrical on the inner and outer peripheral sides. in this case,
Since the movement of grease can be promoted for the inner and outer rings under almost the same conditions, whether grease is filled in the inner raceway groove or grease is filled in the outer raceway groove,
The same effect can be obtained.

Further, preferably, the distance from the inner flat portion of the seal member to the ball crest portion is equal to or more than the distance from the tip of each inclined portion of the seal member to the corresponding raceway groove shoulder portion of each inner and outer race. In this case, the grease accumulated on the shoulder surface of the bearing ring can be more positively moved to the seal member side and adhered thereto.

[0015]

DETAILED DESCRIPTION OF THE INVENTION An embodiment of the present invention will be described in detail below with reference to the accompanying drawings. << Embodiment 1 >> FIG. 1 is an enlarged sectional view of an essential part of a ball bearing according to a first embodiment of the present invention. As shown in FIG. 1, the ball bearing 10 according to the first embodiment includes an inner ring 12 and an outer ring 13 each having raceway grooves 12a and 13a on an outer peripheral surface and an inner peripheral surface, and a raceway groove 12a of the inner and outer rings 12 and 13. , 13a, a plurality of balls 14 that roll in the pockets, a crown type cage 15 that holds the balls 14 in each pocket at a predetermined interval in the circumferential direction, and a bearing axial direction (in the figure, (Up and down direction)
And a seal member 16 attached to the opening portions at both ends.

In the ball bearing 10 of this embodiment, the inner and outer races 1
Seal grooves 12s and 13s are provided in 2 and 13, and the outer peripheral end of the seal member 16 is crimped to the seal groove 13s of the outer ring 13. The seal member 16 is a shield made of iron which is pressed into a cross-sectional shape in which the radially intermediate portion of the annular plate is bulged to the outside, and the inner and outer peripheral end portions thereof have corresponding shoulder surfaces 12b of the inner and outer rings 12, 13. Inclined portion 16a, 1 having an inner side surface inclined at an angle of approximately 45 degrees toward 13b
6b, and a flat portion 16c perpendicular to the axial direction of the bearing is provided between the inclined portions 16a and 16b on the inner and outer circumferences. In addition, the tip portion 16d of the main sealing member 16 is
Is not in contact with the end surface of the shoulder surface 12b.

Further, the sealing member 16 is symmetrical in radial cross-section on the inner and outer peripheral sides except for the caulking portion at the outer peripheral end. Further, the distance B from the inner flat portion 16c of the seal member 16 to the top of the ball 14 is determined from the tips of the inclined portions 16a, 16b of the seal member 16 to the corresponding raceway grooves 12a, 13a of the inner and outer races 12, 13. The dimensions are set so that the distance A to the shoulder portion is not less than A.

Next, a description will be given of the flow mode of the grease when the raceway groove 13a of the outer ring 13 of the ball bearing 10 is filled with grease G of about 30% of the bearing internal space volume and used for inner ring rotation. The white arrow in the figure indicates the moving direction of the grease G.

First, the grease G sealed in the raceway groove 13a has a surplus due to the application of preload.
It is pushed out from a and moves to the shoulder surface 13b of the outer ring 13 to be deposited. Further, the rotation of the inner ring 12 causes the outer ring 13 to rotate.
The grease G that has moved to the shoulder surface 13b of the ball moves to the vicinity of the apex of the rotation axis of the ball 14 and further moves to the shoulder surface 12b of the inner ring 12 to be deposited.

Further, these greases G are used for the inner and outer rings 1
From the ends of the shoulder surfaces 12b and 13b of the seal members 2 and 13, the seal member 1
6 moves toward the seal member 16 side along the inner side surfaces of the inclined portions 16a and 16b of No. 6, and accumulates near the inner surface of the flat portion 16c of the seal member 16. Therefore, the ball bearing 10 of the present embodiment is
Since the grease G can be held in the space away from the balls 14 and the grease G can be prevented from abruptly moving into the raceway grooves 12a and 13a and the pockets, low torque and low torque fluctuation, In addition, high rotation accuracy can be achieved.

In addition, the base oil oozes out from the grease G accumulated on the seal member 16 side, and the inclined portions 16a, 16
Since it enters the raceway grooves 12a, 13a along the inclination of b, it is possible to stably supply the lubricating oil to the inner and outer raceways, and improve the rotational performance of the bearing.

Further, the seal member 16 according to the ball bearing 10 of the present embodiment has a symmetrical radial cross-section on the inner and outer peripheral sides, so that the grease G of the inner and outer races 12 and 13 is substantially the same. Movement can be facilitated.
Therefore, the same effect can be obtained whether grease G is filled in the raceway groove 12a of the inner ring 12 or grease G is filled in the raceway groove 13a of the outer ring 13.

The flat portion 16c of the seal member 16
The distance B from the inner surface of the ball to the top of the ball 14 is the seal member 1
Since the distance A from the tip of each inclined portion 16a, 16b of 6 to the shoulder portion of the corresponding raceway groove 12a, 13a of each inner / outer ring 12, 13 is set to be more positive, The movement of the grease G can be promoted.

<Embodiment 2> FIG. 2 is an enlarged cross-sectional view of a main part of a ball bearing according to a second embodiment of the present invention. As shown in FIG. 2, the ball bearing 20 according to the second embodiment includes an inner ring 22 and an outer ring 23 each having raceway grooves 22a and 23a on the outer and inner circumferential surfaces, and a raceway groove 22 of the inner and outer races 22 and 23, respectively.
a, 23a, a plurality of balls 14, a crown type cage 15 that holds each ball 14 at a predetermined interval in the circumferential direction by accommodating the ball 14 in each pocket, and the axial direction of the bearing (in the figure). , The vertical direction) and the seal member 2 attached to both end openings.
6 and 6.

In the ball bearing 20 of this embodiment, the seal groove 23s is formed only in the outer ring 23, and the outer peripheral end of the seal member 26 is caulked to the seal groove 23s. The inner and outer peripheral ends of the seal member 26 are provided with inclined portions 26a and 26b similar to those of the first embodiment, and the inclined portions 26a and 26b
A flat portion 26c is formed between b. The tip of the inclined portion 26a is not in contact with the inner ring 22. Therefore, also in the ball bearing 20 of the second embodiment, it is possible to obtain the same effect as that of the ball bearing 10 of the first embodiment.

<Third Embodiment> FIG. 3 is an enlarged sectional view of a main part of a ball bearing according to a third embodiment of the present invention. As shown in FIG. 3, the ball bearing 30 according to the third embodiment includes an inner ring 32 and an outer ring 33 having raceway grooves 32a and 33a on the outer and inner circumferential surfaces, and a raceway groove 32 of the inner and outer races 32 and 33, respectively.
a, 33a, a plurality of balls 14 rolling, a crown type cage 15 for holding the balls 14 in each pocket at predetermined intervals in the circumferential direction by accommodating the balls 14 in each pocket, and an axial direction of the bearing (in the figure). , The up and down direction) seal members 3 attached to both end openings
6 and 6.

In the ball bearing 30 of this embodiment, the inner and outer races 3
The seal grooves 32s and 33s are formed in 2 and 33,
As the seal member 36, an iron shield 36d integrally formed with a resin portion 36e on the outer peripheral end is used. In this seal member 36, inclined portions 36a and 36b are formed on the inner peripheral end of the shield 36d and the inner surface of the resin portion 36e, and a flat portion 36c is formed between the inclined portions 36a and 36b.

The inclined portion 36 provided on the resin portion 36e
The tip of b hits the end of the shoulder surface 33b of the outer ring 33. On the other hand, the tip 36f of the iron shield is attached to the inner ring 3
It is not in contact with the end surface of the second shoulder surface 32b. Therefore, also in the ball bearing 30 of the third embodiment, the first bearing
The same effect as the ball bearing 10 of the embodiment can be obtained.

<< Embodiment 4 >> FIG. 4 is an enlarged sectional view of a main part of a ball bearing according to a fourth embodiment of the present invention. As shown in FIG. 4, the ball bearing 40 according to the fourth embodiment includes an inner ring 42 and an outer ring 43 having raceway grooves 42a and 43a on the outer and inner circumferential surfaces, and a raceway groove 42 of the inner and outer races 42 and 43, respectively.
a, 43a, a plurality of balls 14 rolling, a crown type cage 15 that holds the balls 14 in each pocket at a predetermined interval in the circumferential direction by accommodating the balls 14 in each pocket, and the axial direction of the bearing (in the figure). , The up and down direction) seal members 4 attached to both end openings
6 and 6.

In the ball bearing 40 of this embodiment, the seal groove 43s is formed only in the outer ring 43, and the seal member 46 is formed.
As the outer peripheral end of the iron shield 46d, a resin portion 46e is integrally formed. This seal member 46
Then, the inclined portions 46a and 46b are formed on the inner peripheral end of the shield 46d and the inner surface of the resin portion 46e.
A flat portion 46c is formed between 46b.

Further, the inclined portion 46 provided on the resin portion 46e
The tip of b hits the end of the shoulder surface 43b of the outer ring 43. On the other hand, the tip of the inclined portion 46a is not in contact with the inner ring 42. Therefore, the ball bearing 40 of the fourth embodiment
Also in the above, the same operational effects as those of the ball bearing 10 of the first embodiment can be obtained.

<Embodiment 5> FIG. 5 is an enlarged sectional view of a main part of a ball bearing according to a fifth embodiment of the present invention. As shown in FIG. 5, the ball bearing 50 according to the fifth embodiment includes an inner ring 52 and an outer ring 53 having raceway grooves 52a and 53a on the outer peripheral surface and the inner peripheral surface, respectively, and a raceway groove 52 of the inner and outer races 52 and 53.
a, 53a, a plurality of balls 14 rolling, a crown type cage 15 that holds each ball 14 at a predetermined interval in the circumferential direction by accommodating the ball 14 in each pocket, and an axial direction of the bearing (in the figure). , The vertical direction) and the seal member 5 attached to both end openings.
6 and 6.

In the ball bearing 50 of this embodiment, the inner and outer races 5 are
The seal grooves 52s and 53s are formed in 2, 53,
As the sealing member 56, the resin portion 56 is provided around the core metal 56d.
An elastic seal integrally formed with e and 56f is used.
In this seal member 56, the resin portion 56 provided at the inner and outer peripheral ends
The inclined portions 56a and 56b are formed on the inner surfaces of the e and 56f, and the flat portion 56c is formed between the inclined portions 56a and 56b.

Also, the inclined portion 56 provided on the resin portion 56f
The tip of b is abutted against the end of the shoulder surface 53b of the outer ring 53, but the tip of the inclined portion 56a provided on the resin portion 56e is not in contact with the end surface of the shoulder surface 52b of the inner ring 52. . Therefore, also in the ball bearing 50 of the fifth embodiment,
It is possible to obtain the same effects as those of the ball bearing 10 of the first embodiment.

<< Embodiment 6 >> FIG. 6 is an enlarged sectional view of a main part of a ball bearing according to a sixth embodiment of the present invention. As shown in FIG. 6, the ball bearing 60 according to the sixth exemplary embodiment includes an inner ring 62 and an outer ring 63 each having raceway grooves 62a and 63a on the outer peripheral surface and the inner peripheral surface, and a raceway groove 62 of the inner and outer races 62 and 63.
a, 63a, a plurality of balls 14 rolling, a crown type cage 15 that holds the balls 14 in each pocket at a predetermined interval in the circumferential direction, and a ball-shaped axial direction of the bearing (in the figure). , The vertical direction) and the seal member 6 attached to both end openings.
6 and 6.

In the ball bearing 60 of this embodiment, the seal groove 63s is formed only in the outer ring 63, and the seal member 66 is formed.
An elastic seal in which resin portions 66e and 66f are integrally formed around a cored bar 66d is used as. This seal member 6
6, the slanted portions 66a and 66b are formed on the inner surfaces of the resin portions 66e and 66f provided at the inner and outer peripheral ends.
A flat portion 66c is formed between 66b.

Further, the inclined portion 66 provided on the resin portion 66f
The tip of b is abutted against the end of the shoulder surface 63b of the outer ring 63, but the tip of the inclined portion 66a provided on the resin portion 66e is located close to the shoulder surface 62b of the inner ring 62. It is not in contact with the surface 62b. Therefore, also in the ball bearing 60 of the sixth embodiment, it is possible to obtain the same effect as that of the ball bearing 10 of the first embodiment.

<< Embodiment 7 >> FIG. 7 is an enlarged cross-sectional view of a main part of a ball bearing according to a seventh embodiment of the present invention. As shown in FIG. 7, the ball bearing 70 according to the seventh embodiment includes an inner ring 72 and an outer ring 73 having raceway grooves 72a and 73a on the outer peripheral surface and an inner peripheral surface, respectively, and a raceway groove 72 of the inner and outer races 72 and 73.
a, 73a, a plurality of balls 14, a crown type cage 15 that holds the balls 14 in each pocket at a predetermined interval in the circumferential direction by accommodating the balls 14 in each pocket, and the axial direction of the bearing (in the figure). , The up and down direction) seal members 7 attached to both end openings
6 and 6.

In the ball bearing 70 of this embodiment, the outer ring 673 is
The seal groove 73s is formed only in the
As 6, an elastic seal in which resin parts 76e and 76f are integrally formed around a core metal 76d is used. In this seal member 76, inclined portions 76a and 76b are formed on the inner surfaces of the resin portions 76e and 76f provided at the inner and outer peripheral ends, and the inclined portion 76 is formed.
A flat portion 76c is formed between a and 76b.

Further, the inclined portion 76 provided on the resin portion 76e
The tip of a is made close to the shoulder surface 72b of the inner ring 72, but is not in contact with the shoulder surface 72b.
The tip portion 76g of the inclined portion 76b provided on the upper portion extends to a position where it covers the shoulder surface 73b of the outer ring 73, so that the grease easily moves to the inclined portion 76b side. Therefore, also in the ball bearing 70 of the seventh embodiment, it is possible to obtain the same effects as those of the ball bearing 10 of the first embodiment.

In each of the above-mentioned embodiments, the place where grease is filled is the raceway groove of the outer ring, but the same effect is obtained when grease is filled in the raceway groove of the inner ring.
Further, the inclination angle of the inclined portion provided on the inner and outer peripheral ends of the seal member with respect to the shoulder surface of the bearing ring is appropriately changed depending on the physical properties of the grease and the like. Further, in the above embodiment, the seal member is an iron press-molded product such as a shield or an elastic seal obtained by integrally molding a resin on a core metal, but a plastic integrally-molded product or the like can be adopted, and the material is There is no particular limitation.

Further, by applying the present invention, in addition to the above-described effects, the effect of suppressing grease leakage between the inner ring and the seal member and the effect of sealing the gap between the inner ring and the seal member with grease are expected. can do. In each of the above embodiments, the seal member has a so-called non-contact type that does not come into contact with the inner ring. However, if a more sealing effect is required, the seal member is not limited to this, and a contact type It may be shaped.

[0043]

As described above, according to the ball bearing of the present invention, the inner and outer peripheral ends of the seal member on the pocket opening side of the crown type cage are directed toward the shoulder surfaces of the corresponding inner and outer rings. An inclined portion is formed with an inclined inner surface. Therefore, the grease accumulated on the shoulder surface of the bearing ring can be positively moved to the seal member side and adhered thereto.

Since the grease is secured in the space away from the balls and the sudden movement of the grease into the raceway grooves and pockets is prevented, balls with low torque, low torque fluctuation, and high rotation accuracy are provided. A bearing can be realized. or,
The base oil oozes out from the grease accumulated on the seal member side and enters the raceway groove along the inclination of the inclined part, so a stable supply of lubricating oil is possible and the rotation performance of the bearing is improved. Can be achieved.

[Brief description of drawings]

FIG. 1 is an enlarged cross-sectional view of a main part of a ball bearing according to a first embodiment of the present invention.

FIG. 2 is an enlarged sectional view of a main part of a ball bearing according to a second embodiment of the present invention.

FIG. 3 is an enlarged sectional view of a main part of a ball bearing according to a third embodiment of the present invention.

FIG. 4 is an enlarged sectional view of a main part of a ball bearing according to a fourth embodiment of the present invention.

FIG. 5 is an enlarged sectional view of a main part of a ball bearing according to a fifth embodiment of the present invention.

FIG. 6 is an enlarged sectional view of a main part of a ball bearing according to a sixth embodiment of the present invention.

FIG. 7 is an enlarged sectional view of a main part of a ball bearing according to a seventh embodiment of the present invention.

FIG. 8 is an enlarged sectional view of a main part of a conventional ball bearing.

FIG. 9 is an enlarged sectional view of a main part of another conventional ball bearing.

FIG. 10 is an enlarged sectional view of a main part of another conventional ball bearing.

[Explanation of symbols]

12 inner ring 12a Track groove 12b Shoulder 13 outer ring 13a Track groove 13b Shoulder 14 balls 15 Crown type cage 10 ball bearings 16 Seal member 16a, 16b inclined portion 16c flat part

   ─────────────────────────────────────────────────── ─── Continued front page    F-term (reference) 3J016 AA02 BB15 BB16 CA01                 3J101 AA02 AA32 AA42 AA62 BA24                       BA73 EA63 FA60 GA28

Claims (3)

[Claims] 1. A plurality of balls rollable between an inner ring and an outer ring are held in respective pockets of a crown type cage and arranged at predetermined intervals in the circumferential direction, and openings at both ends in the axial direction. A ball bearing to which a seal member is attached, wherein at least the inner and outer peripheral ends of the seal member located at the pocket opening side of the crown-shaped cage are inclined toward the shoulder surfaces of the corresponding inner and outer rings. A ball bearing, wherein an inclined portion having an inner surface is formed. 2. The radial cross-sectional shape of the seal member is
The ball bearing according to claim 1, wherein the inner and outer peripheral sides have a symmetrical shape. 3. The distance from the inner flat portion of the seal member to the ball crest is equal to or greater than the distance from the tip of each inclined portion of the seal member to the corresponding track groove shoulder portion of each inner and outer ring. The ball bearing according to claim 1 or 2, which is characterized.