JP2009275799A - Deep groove ball bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a deep groove ball bearing capable of reducing bearing torque. <P>SOLUTION: The deep groove bearing 10 is provided with an inner ring 12, an outer ring 11, a plurality of balls 13 rollable in a circumference direction between the inner ring 12 and the outer ring 11, a resin retainer 20 holding the balls 13 in pockets 25, and is used with oil lubrication. An oil reservoir plate 14 extending radially inward is provided at axial direction both end parts of the outer ring 11. The retainer 20 comprises two synthetic resin annular elements 20a, 20b. The annular elements 20a, 20b are provided with annular parts 21a, 21b and a plurality of column parts 22a, 22b projecting from the annular part 21a, 21b in an axial direction. A plurality of semi-spherical pockets 25a, 25b following an outer circumference of the balls 13 are formed on opposing surfaces of the adjacent column parts. Axial direction dimensions of the retainer 20 are constant over whole circumference. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a deep groove ball bearing used for high-speed operation, for example, in an automobile transmission.

  As a resin cage generally used in a deep groove ball bearing, for example, there is a cage 101 called a crown type cage shown in FIG. The cage 101 is formed by injection molding of synthetic resin, and an annular rim portion 102 and a plurality of pillar portions arranged at predetermined intervals in the circumferential direction on the axial end surface of the rim portion 102. 103, a pocket portion 104 formed between the pillar portions 103 and 103 so as to be adjacent to each other, and holds a plurality of balls so as to be able to roll in the circumferential direction at substantially equal intervals, and a circle on the inner peripheral surface of the pocket portion 104 A pair of claw portions 105a and 105b formed at both ends in the circumferential direction, and an opening portion 106 formed between the tips of the pair of claw portions 105a and 105b. Then, by pushing the ball into the pocket 104 while expanding the pair of claws 105a and 105b from the opening 106, the ball is held in the pocket 104 so as to be able to roll through a minute gap.

  However, the crown type cage 101 incorporated in the conventional deep groove ball bearing is a ball guide type cage, and the end portion on the pocket inner diameter side comes into contact with the ball 107 in response to the recent high speed rotation. By wearing, as shown in FIG. 13, the centrifugal force due to the rotation of the cage 101 acts on the axial end portion 108 on the cage opening side, and the elasticity or the axial end portion 109 on the rim side is used as the torsion axis. Torsional deformation due to plastic deformation may occur, and the cage outer diameter surface may come into contact with the inner diameter surface of the outer ring, causing the cage to wear, and problems such as abnormal heat generation and increased torque may occur.

  As a bearing for high-speed rotation, as shown in FIG. 14, Patent Document 1 discloses that the spherical center P of the pocket of the crown-shaped cage 110 is positioned on the outer diameter side from the thickness center C in the cage radial direction, A bearing that secures the quantity is disclosed. Thereby, the torsional deformation of the cage 110 toward the outer diameter side is suppressed, and sliding between the cage 110 and the outer ring is prevented.

Patent Document 2 discloses a corrugated cage 112 in which two annular elements 111, 111 are combined for the purpose of suppressing torsional deformation as shown in FIG.
Japanese Utility Model Publication No. 5-34317 JP 2003-343571 A

  However, even when the bearing having the crown type cage described in Patent Document 1 is rotated at high speed, the pocket inner diameter side becomes worn due to the lack of oil due to centrifugal force, and eventually the torsional deformation cannot be suppressed. There is a possibility that 110 may slide on the outer ring and swing around. When the swinging occurs, an abnormal force is applied to the cage 110, and the cage may be damaged.

  Further, the crown type cage 110 has a problem that the bearing torque increases because the oil contacts the recess indicated by the arrow A in FIG.

  In the structure described in Patent Document 2 as well, at the time of high-speed rotation, insufficient lubrication occurs between the inner diameter side of the cage and the ball sliding portion due to centrifugal force, and wear occurs in this portion. Could occur. Furthermore, in this corrugated cage, the recesses indicated by arrows B in FIG. 15 are formed on both sides of the ball, so that the agitation resistance of the lubricating oil is increased and the bearing torque is high compared to the crown cage. There were drawbacks. In order to prevent wear of the cage, the cage may be a cylindrical pocket instead of a spherical pocket and used as an outer ring guide, but it is desirable because the torque increases due to sliding between the cage and the outer ring. Absent.

  The present invention has been made to eliminate such inconveniences, and an object of the present invention is to provide a deep groove ball bearing capable of reducing bearing torque.

The above object of the present invention is achieved by the following configurations.
(1) Oil lubrication comprising an inner ring, an outer ring, a plurality of balls capable of rolling in a circumferential direction between the inner ring and the outer ring, and a resin cage containing the balls in a pocket. A deep groove ball bearing used,
At both ends in the axial direction of the outer ring, oil retaining portions extending radially inward are provided,
The cage is composed of two synthetic resin annular elements,
Each annular element includes an annular part and a plurality of pillars protruding in the axial direction from the annular part, and a hemispherical pocket following the outer periphery of the ball is formed in the adjacent pillar part,
A deep groove ball bearing characterized in that the axial dimension of the cage is uniform over the entire circumference.
(2) The deep groove ball bearing according to (1), wherein a radial dimension of the column part is larger than a radial dimension of the annular part in an axial section of the cage.
(3) The deep groove ball bearing according to (1) or (2), wherein notches for supplying or discharging oil are provided on both axial sides of the outer peripheral surface of the inner ring.
(4) The deep groove ball bearing according to any one of (1) to (3), wherein an inner diameter dimension of the oil retaining portion is smaller than a pitch circle diameter of the balls.
(5) The deep groove ball bearing according to any one of (1) to (4), wherein the shortest distance between the outer peripheral surface of the inner ring and the oil retaining portion is 9% or more of the diameter of the ball. .

  According to the deep groove ball bearing of the present invention, oil retaining portions are provided at both ends of the outer ring in the axial direction, and the inside of the bearing is placed in an oil bath so that oil is always distributed to the cage and the sliding portion of the ball. Thus, wear of the cage can be suppressed and swinging can be prevented.

  In addition, the axial dimensions of the cage are uniform over the entire circumference, and there are no irregularities similar to balls on the side surfaces in the axial direction as in conventional crown-type cages and corrugated cages. Can be realized.

  Hereinafter, each embodiment of the deep groove ball bearing according to the present invention will be described in detail with reference to the drawings.

(First embodiment)
1 is a longitudinal sectional view of an essential part of a deep groove ball bearing according to a first embodiment of the present invention, FIG. 2 is an overall perspective view of a cage incorporated in the deep groove ball bearing of FIG. 1, and FIG. It is a fragmentary perspective view of this cage.
The deep groove ball bearing 10 is freely rollable between an outer ring 11 having an outer ring raceway surface 11a on an inner peripheral surface, an inner ring 12 having an inner ring raceway surface 12a on an outer peripheral surface, and the outer ring raceway surface 11a and the inner ring raceway surface 12a. A plurality of balls 13 provided on the outer ring 11, and a synthetic resin cage 20 provided between the inner peripheral surface of the outer ring 11 and the outer peripheral surface of the inner ring 12 to hold the plurality of balls 13 in a rollable manner, and the outer ring 11, and a metal oil retaining plate 14 (oil retaining portion) fixed to grooves 11 b provided at both axial ends of the inner peripheral surface.

  The cage 20 has annular portions 21a and 21b on both sides in the axial direction, and a plurality of column portions that connect the annular portions 21a and 21b to each other at equal intervals in the circumferential direction from a plurality of locations of the annular portions 21a and 21b. 22 is a so-called doubly-supported cage. The end portions of the annular portions 21a and 21b are formed in an arc shape in the axial section of the cage 20, and the distance between the axial ends of the annular portions 21a and 21b, that is, the axial dimension of the cage 20 is It is uniform over the entire circumference of 20. Further, the opposing surface of the column portions 22 adjacent to each other in the circumferential direction is a partial spherical pocket 25 having a radius of curvature slightly larger than that of the ball 13 following the rolling surface of the ball 13, thereby the cage 20. The ball 13 is positioned in the axial direction and the radial direction by the ball 13 and is guided by the ball 13 during rotation.

  Further, convex portions 23 and 24 are provided on the inner diameter side annular surface and the outer diameter side annular surface of the column portion 22, and the radial dimension of the column portion 22 in the axial section of the cage 20 is an annular portion 21 a, It is larger than the radial dimension of 21b. These convex portions 23 and 24 are provided over the entire circumference of the column portion 22 so as to reduce the distance between the cage 20 in the radial direction and the outer ring 11 and the inner ring 12. In the present embodiment, the upper surfaces of the convex portions 23 and 24 have substantially the same radial dimension as the outer peripheral surface of the inner ring 12 and the inner peripheral surface of the outer ring 11. It may be smaller than the outer peripheral surface of the inner ring 12 or larger than the inner peripheral surface of the outer ring 11 so as not to contact the inner ring raceway surface 12a or the outer ring raceway surface 11a.

  The cage 20 is formed of a resin, and as a resin material, a polyamide resin such as polyamide 46 or polyamide 66, polybutylene terephthalate, polyferlen salside (PPS), polyamideimide (PAI), thermoplastic polyimide, polyetheretherketone ( Examples include PEEK) and polyether nitrile (PEN). Moreover, the rigidity and dimensional accuracy of the cage 20 can be improved by appropriately adding about 10 to 50 wt% of a fibrous filler such as glass fiber or carbon fiber to the resin.

In FIG. 4, the disassembled perspective view of each component of the holder | retainer 20 is shown.
The cage 20 is a combination cage composed of a first element 20a (annular element) and a second element 20b (annular element). The first element 20a and the second element 20b include annular portions 21a and 21b and column portions 22a and 22b arranged at predetermined intervals, respectively, and the column portions 22a and 22b and the column portions 22a in the circumferential direction are provided. A plurality of hemispherical pockets 25a and 25b that follow the outer periphery of the ball 13 are provided between 22b.

  A protrusion 26 is formed on the tip surface of each column portion 22a of the first element 20a so as to protrude perpendicularly in the axial direction from the substantially central portion in the circumferential direction, and each column portion 22b of the second element 22b has a substantially central portion in the circumferential direction. A recess 27 that is recessed in the axial direction is provided. When assembling the first element 20a and the second element 20b, the projection 26 of the first element 20a and the recess 27 of the second element 20b are engaged, thereby positioning in the radial direction and the axial direction. The first element 20a and the second element 20b are bonded and fixed by an agent or the like, and are integrally formed. In this way, by combining the first element 20a and the second element 20b, the column portion 22 is configured by the column portions 22a and 22b, and the partial spherical pocket 25 is configured by the hemispherical pockets 25a and 25b.

  The oil retaining plate 14 is formed, for example, by pressing a metal plate material such as SPCC to form a substantially annular shape, and the outer peripheral portion 14 a is provided at the axial end of the inner peripheral surface of the outer ring 11. The inner peripheral portion 14b is press-fitted and fixed in the groove 11b, and is disposed with a clearance from the outer peripheral surface 12b of the inner ring 12. The oil retaining plate 14 may be formed in an overall annular shape by covering a metal core with an elastic material such as rubber or synthetic resin. The gap between the inner peripheral portion 14b of the oil retaining plate 14 and the outer peripheral surface 12b of the inner ring 12 functions as a lubricant supply port or a discharge port.

  The deep groove ball bearing 10 configured as described above has one of the axial directions arranged on the lubricant supply side and the other on the discharge side. For example, the outer ring 11 is fitted in the housing, and the inner ring 12 is fitted on the rotating shaft. The outer ring is fitted and incorporated in a device such as a transmission of an automobile so that the inner ring 12 and the outer ring 11 can freely rotate relative to each other. At this time, each ball 13 revolves around the inner ring 12 while rotating. Further, the cage 20 rotates around the inner ring 12 at the same speed as the revolution speed of each ball 13.

  The space between the housing and the rotating shaft acts as a supply path and a discharge path for supplying and discharging the lubricating oil. When the lubricating oil is supplied from the side of the deep groove ball bearing 10 through a supply path from a lubricating oil tank (not shown), the lubricating oil is supplied to the inner peripheral portion 14 b of the oil retaining plate 14 and the inner ring 12. The lubricant flows into the deep groove ball bearing 10 through the opening 15 with the outer peripheral surface 12 b, and the lubricating oil is stirred by the cage 20 and the balls 13 as the deep groove ball bearing 10 rotates.

  At this time, the lubricating oil supplied to the deep groove ball bearing 10 is blown to the outer diameter side by centrifugal force and blocked by oil retaining plates 14 installed at both ends of the outer ring 11, and the interior of the deep groove ball bearing 10 is It becomes an oil bath state. The lubricating oil lubricates the sliding surfaces of the outer ring 11, the inner ring 12, the balls 13, and the cage 20, and then is discharged from the opening 15 on the side opposite to the opening on the supply side to the discharge path.

  In the deep groove ball bearing 10 of the present invention configured as described above, the axial dimension of the cage 20 is uniform over the entire circumference of the cage 20, and the conventional crown type cage and corrugated type cage are used. Compared to the case, the frictional resistance can be reduced and the bearing torque can be reduced because there is no unevenness on the axial direction side.

  Further, since the deep groove ball bearing 10 uses the cage 20 made of synthetic resin, the inertial mass of the cage itself can be sufficiently reduced, and the bearing weight and the rotational speed are increased accordingly. be able to. The cage 20 made of synthetic resin is economical because it can be mass-produced by injection molding.

  In addition, since the cage 20 has a spherical pocket 25 and is guided by a ball, the cage 20 does not slide with the outer ring 11 or the inner ring 12, so that the torque can be reduced.

  Moreover, since the convex parts 23 and 24 which made the thickness of radial direction larger than the annular parts 21a and 21b are provided in both the inner diameter side annular surface and the outer diameter side annular surface of the pillar part 22 of the cage 20, The distance between the inner diameter side annular surface 23 of the column and the inner ring raceway surface 12a and the distance between the outer diameter side annular surface 24 and the outer ring raceway surface 11a are reduced, and the space where the lubricating oil stays is reduced, thereby reducing the stirring resistance. The bearing torque can be reduced. In the present embodiment, convex portions 23 and 24 having a larger radial thickness than the annular portions 21a and 21b are provided on both the inner diameter side annular surface and the outer diameter side annular surface of the column portion 22. However, you may form only in either one.

  Further, since the first element 20a and the second element 20b constituting the cage 20 are fixed using an adhesive, it is not necessary to process the engaging portions of the elements 20a and 20b in a complicated manner, and the workability is good.

  Further, the oil retaining plate 14 and the inner ring 12 are provided with an opening 15 serving as a lubricating oil supply port or a discharge port, so that the supply and discharge performance of the lubricating oil is not impaired. The temperature increase of the deep groove ball bearing 10 can be suppressed without continuing to stay. Thereby, since lubricating oil always exists in the sliding part of the cage 20 and the ball 13 and the cage 20 and the outer ring 11, the lubricity of the sliding part is improved, wear is suppressed, and the cage 20 Swinging can be prevented.

<Modification 1>
FIG. 5 is a partial perspective view showing a modified example of the cage 20. The cage 20A of Modification 1 is the same as the cage 20 except that the method of fixing the first element 20a and the second element 20b is different from the cage 20 of the deep groove ball bearing 10 of the first embodiment. The same components as those in FIG.

  The annular portions 21a and 21b and the column portions 22a and 22b of the first element 20a and the second element 20b constituting the cage 20A are provided with through holes 33 penetrating in the axial direction. As shown in FIG. The first element 20a and the second element 20b are fixed by attaching the nut 34 to the nut and inserting the socket bolt 35 from the other side and screwing it into the nut 34. In consideration of the balance in the axial direction, the socket bolts 35 and the nuts 34 are alternately arranged in the circumferential direction. Thereby, the 1st element 20a and the 2nd element 20b can be fixed reliably, and also the 1st element 20a and the 2nd element 20b can be made into the same shape.

<Modification 2>
FIG. 6 is a partial perspective view showing another modified example of the cage 20. The cage 20B of Modification 2 is the same except that the fixing method of the first element 20a and the second element 20b is different from the cage 20 of the deep groove ball bearing 10 of the first embodiment. The same components as those in FIG.

  As shown in FIG. 6 (a), a protrusion 46 protruding perpendicularly from the circumferential center to the axial direction is provided on the front end surface of each column portion 22a of the first element 20a constituting the cage 20B. At the tip of the portion 46, a flange 47 is formed that slightly protrudes from the outer diameter surface of the protrusion to the outer diameter side.

  Each column portion 22b and the annular portion 21b of the second element 20b constituting the cage 20B are provided with through holes 48 penetrating in the axial direction. When the first element 20a and the second element 20b are assembled, the first element A step portion (not shown) that engages with the flange portion is formed approximately in the middle of the wall portion facing the flange portion 20a in the axial direction.

  In this modification, the protrusion 47 of the first element 20a is inserted into the through hole 48 of the second element 20b, and the flange 47 of the first element 20a is engaged with the step of the second element 20b. The first element 20a and the second element 20b are fixed. According to this, although the process of an engaging part becomes complicated, the 1st element 20a and the 2nd element 20b can be fixed reliably, without using an adhesive agent.

(Second Embodiment)
FIG. 7 is a longitudinal sectional view of an essential part of a deep groove ball bearing according to the second embodiment of the present invention. In the figure, the same components as those of the first embodiment are denoted by the same reference numerals and description thereof is omitted.

  In this embodiment, as shown to Fig.7 (a), instead of the oil retaining plate 14 of 1st Embodiment, the protrusion part 50a which protrudes in the inside of a bearing in the housing 50 which fits the outer ring | wheel 11A of the deep groove ball bearing 10A is carried out. And a protrusion 51a that protrudes into the bearing is provided on the housing lid 51 that covers the opposite side of the deep groove ball bearing 10A in the axial direction, and these protrusions 50a and 51a function as oil retaining portions.

  Moreover, as shown in FIG.7 (b), as a separate member between the housing 50 and the housing cover 51 which fit the outer ring | wheel 11A of the deep groove ball bearing 10B instead of the oil retaining plate 14 of 1st Embodiment, It is also possible to insert annular plates 52 and 53 provided with projecting portions 52a and 53a projecting inside the bearing, and to make these projecting portions 52a and 53a function as oil retaining portions.

  Thereby, the function similar to the oil retaining plate 14 in the first embodiment can be given to the housing 50 (housing lid body 51) or the annular plates 52, 53, and the groove 11b for the oil retaining plate 14 is formed in the outer ring 11A. A general-purpose outer ring can be used without having to do so.

(Third embodiment)
FIG. 8 is a longitudinal sectional view of an essential part of a deep groove ball bearing according to a third embodiment of the present invention. The deep groove ball bearing of the third embodiment is the same as the deep groove ball bearing of the first embodiment except that the shape of the inner ring is different. In the figure, the same components as those of the first embodiment are denoted by the same reference numerals and description thereof is omitted.

  The deep groove ball bearing 10C of the third embodiment shown in FIG. 8 (a) is notched at both ends in the axial direction of the outer peripheral surface 12b of the inner ring 12A in order to secure an opening 15 serving as a lubricant supply or discharge port. Thus, the tapered surface 12c is formed to increase the opening area. Further, the deep groove ball bearing 10D shown in FIG. 8B is notched at both axial end portions of the outer peripheral surface 12b of the inner ring 12B so as to secure the opening 15 serving as a lubricant supply or discharge port. 12d is formed to increase the opening area.

  In order to secure the oil bath portion, it is desirable to reduce the inner diameter dimension of the oil retaining plate 14, but if the difference between the inner diameter 14b of the oil retaining plate 14 and the outer peripheral surface 12b of the inner ring 12 is too small, supply and discharge of lubricating oil is performed. The bearing temperature rises without impairing performance. Therefore, by notching at both ends in the axial direction of the outer peripheral surface 12b of the inner ring 12, the opening area of the opening 15 is secured to prevent the lubricating oil from staying and the temperature of the deep groove ball bearings 10C and 10D is increased. Can be suppressed.

Next, examples of the deep groove ball bearing according to the present invention will be described.
[Example 1]
[Cage swing comparison test]
Using the deep groove ball bearing shown in FIG. 9 (same as the deep groove ball bearing of FIG. 8B), the inner diameter dimension of the oil retaining plate (oil retaining plate inner diameter Ds: 65 mm) is fixed and the outer diameter of the inner ring end ( Time until the opening amount (y) of the opening portion is changed by changing Di) and the whirling to the opening ratio (y / Dw), which is the ratio of the opening amount (y) to the ball diameter (Dw), occurs. Was determined under the following conditions. As a comparative example, a crown type resin cage having the same specifications was used except for the cage shape, and the test was performed under the same test conditions.
<specification>
Bearing name number: Single row deep groove ball bearing 6011 manufactured by NSK Ltd.
Ball pitch circle diameter: 72.5mm
Cage: Resin cage with spherical pocket combination Cage material: Polyamide 46 (15% carbon fiber filling)
Oil retaining plate: SPCC is press-molded and crimped to the outer ring end.

<Test conditions>
Lubrication method: VG24 mineral oil forced lubrication Oil amount: 0.1 L / min
Lubrication temperature: 120 ° C
Rotation speed: 30000rpm
Load: 2000N
Test time: 20 hours, 50 hours, 100 hours, and then measuring the presence or absence of swinging every 100 hours

  The results of the cage run-out comparison test are shown in Table 1 and FIG. From the results of this cage runout comparison test, it was found that the cage runout start time was significantly increased in the case of the spherical pocket combination cage of this example compared to the crown type cage which is a comparative example. .

  Further, when the aperture ratio (y / Dw) is 9% or more, the improvement of the swing start time of the spherical pocket combination holder of this embodiment is almost saturated, and when the aperture ratio (y / Dw) is 11% or more, In the spherical pocket combination cage of the embodiment, the swing start time is completely saturated. Accordingly, the opening ratio (y / Dw) is preferably 9% or more, and more preferably 11% or more.

[Example 2]
[Cage swing comparison test 2]
With the same specifications and test conditions as in Example 1, the opening amount (y: 1.14 mm) of the opening is fixed, and the inner diameter dimension (Ds) of the oil retaining plate is changed as shown in Table 2, The time until the whirling with respect to the difference between the inner diameter dimension (Ds) and the pitch circle diameter (Dpcd) of the balls occurred. The outer diameter of the inner ring end was separately provided with an annular shielding plate at the inner ring end, and the test was conducted assuming that the outer diameter of the shielding plate was the outer diameter of the inner ring.

  The results of the cage run-out comparison test are shown in Table 2 and FIG. From the results of this cage runout comparison test, it was found that the cage runout start time was significantly increased in the case of the spherical pocket combination cage of this example compared to the crown type cage which is a comparative example. .

  Further, if the oil retaining plate inner diameter is larger than the pitch pitch diameter Dpcd of the ball, an opening exists on the outer diameter side, so that a larger centrifugal force acts on the opening and the lubricating oil on the inner diameter side of the oil retaining plate is moved outside the bearing. To be skipped. Therefore, the oil bath state cannot be formed in the sliding portion with the ball on the inner diameter side of the cage, and the effect of suppressing the swinging is reduced due to wear. On the other hand, when the oil retaining plate inner diameter is set to be equal to or less than the pitch circle diameter Dpcd of the ball, a whirling prevention effect appears, and when the oil retaining plate inner diameter is made equal to or less than the cage inner diameter, the whirling prevention effect is saturated.

  From the above results, if the oil retaining plate inner diameter is equal to or less than the pitch circle diameter of the ball, the lubricating oil can be maintained in the oil bath state between the cage and the ball. The inner diameter or less is more preferable.

[Example 3]
[Bearing torque comparison test]
Using the deep groove ball bearing shown in FIG. 9 (same as the deep groove ball bearing of FIG. 8B), the inner diameter dimension of the oil retaining plate (oil retaining plate inner diameter Ds: 65 mm) was fixed, and the bearing torque was measured. As a comparative example, a crown type resin cage with an oil retaining plate and a crown type resin cage without an oil retaining plate of the same specification except for the shape of the cage were used, and the test was performed under the same test conditions.
<specification>
Bearing name number: Single row deep groove ball bearing 6011 manufactured by NSK Ltd.
Ball pitch circle diameter: 72.5mm
Cage: Resin cage with spherical pocket combination Cage material: Polyamide 46 (15% carbon fiber filling)
Cage inner diameter: 68.3 mm
Oil retaining plate: SPCC is press-molded and crimped to the outer ring end. Oil retaining plate inner diameter: 65 mm
Aperture ratio (y / Dw): 11%

<Test conditions>
Lubrication method: VG24 mineral oil forced lubrication Oil amount: 0.25 L / min
Lubrication temperature: 110 ° C
Rotation speed: 9000rpm
Load: 300N

  Table 3 shows the results of the bearing torque comparison test. From the results of this bearing torque comparison test, in the case of the spherical pocket combination resin retainer of the present invention which does not have the uneven shape due to the claw, compared to the crown type retainer provided with the oil retaining plate as a comparative example, the bearing torque is It was possible to reduce. Further, even in the case of the spherical pocket combination retainer of the present example, the bearing torque could be reduced even when compared with the crown retainer that does not include the oil retaining plate as a comparative example.

  In addition, this invention is not limited to embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably. In addition, the material, shape, dimension, numerical value, form, number, arrangement location, and the like of each component in the above-described embodiment are arbitrary and are not limited as long as the present invention can be achieved.

It is a principal part longitudinal cross-sectional view of the deep groove ball bearing which is 1st Embodiment of this invention. It is a whole perspective view of the holder | retainer integrated in the deep groove ball bearing of FIG. It is a fragmentary perspective view of the holder | retainer of FIG. 2 provided with the ball | bowl. FIG. 3 is a partially exploded perspective view of the cage in FIG. 2. It is a fragmentary perspective view which shows the modification of a holder | retainer. It is a fragmentary perspective view which shows the other modification of a holder | retainer. It is a principal part longitudinal cross-sectional view of the deep groove ball bearing which is 2nd Embodiment of this invention. It is a principal part longitudinal cross-sectional view of the deep groove ball bearing which is 3rd Embodiment of this invention. It is principal part sectional drawing of the deep groove ball bearing of this invention used for a cage swaying comparison test. It is a graph which shows the test result of a cage swing comparison test 1. It is a graph which shows the test result of a cage swing comparison test 2. It is a perspective view of the conventional crown type resin retainer for deep groove ball bearings. It is principal part sectional drawing for demonstrating the malfunction of the rolling bearing incorporating the conventional crown type cage for rolling bearings. It is explanatory drawing of the crown type cage for rolling bearings described in Patent Document 1. It is explanatory drawing of the corrugated cage for rolling bearings described in Patent Document 2.

Explanation of symbols

10, 10A, 10B, 10C, 10D Deep groove ball bearing 11 Outer ring 12 Inner ring 13 Ball 14 Oil retaining plate (oil retaining portion)
20, 20A, 20B Cage 21a First element (annular element)
21b Second element (annular element)
23, 24 Convex part (Cage convex part)
25 pockets

Claims (5)

Used in oil lubrication provided with an inner ring, an outer ring, a plurality of balls that can roll in a circumferential direction between the inner ring and the outer ring, and a resin cage containing the balls in a pocket. Deep groove ball bearing,
At both ends in the axial direction of the outer ring, oil retaining portions extending radially inward are provided,
The cage is composed of two synthetic resin annular elements,
Each annular element includes an annular portion and a plurality of column portions that protrude in the axial direction from the annular portion, and a plurality of hemispherical pockets that follow the outer periphery of the ball are formed on opposing surfaces of the adjacent column portions. Formed,
A deep groove ball bearing characterized in that the axial dimension of the cage is uniform over the entire circumference.   2. The deep groove ball bearing according to claim 1, wherein a radial dimension of the column portion is larger than a radial dimension of the annular portion in an axial cross section of the cage.   The deep groove ball bearing according to claim 1 or 2, wherein notches for supplying or discharging oil are provided on both axial sides of the outer peripheral surface of the inner ring.   The deep groove ball bearing according to any one of claims 1 to 3, wherein an inner diameter of the oil retaining portion is smaller than a pitch circle diameter of the balls.   The deep groove ball bearing according to any one of claims 1 to 4, wherein the shortest distance between the outer peripheral surface of the inner ring and the oil retaining portion is 9% or more of the diameter of the ball.

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