JP5012500B2 - Deep groove ball bearing - Google Patents

Description

  The present invention relates to a deep groove ball bearing used for high-speed rotation, such as an automobile transmission, for example, in particular in a forced lubrication system in which lubricating oil is supplied from the outside of the bearing to the inside of the bearing by a pump or the like. The present invention relates to a deep groove ball bearing used in an oil lubricated environment.

  As shown in FIG. 15, the conventional deep groove ball bearing includes an inner ring 101 having an inner ring raceway groove 101a on the outer peripheral surface, an outer ring 102 having an outer ring raceway groove 102a on the inner peripheral surface, an inner ring raceway groove 101a and an outer ring raceway groove 102a. A plurality of balls 103 that are arranged so as to be freely rollable between each other, an annular portion 104a, and a plurality of column portions 104b that protrude from one axial end face of the annular portion 104a. And a crown-shaped cage 104 that accommodates the ball 103 in a spherical pocket 104c formed between 104b. The balls 103 are held at predetermined intervals in the circumferential direction by the cage 104 and revolve with the cage 104.

  Such deep groove ball bearings are often lubricated by a forced lubrication system in which lubricating oil is supplied by a pump or the like when used in a rotating part of an automobile transmission or the like. In the axial direction and circulates in the transmission unit.

  By the way, when this deep groove ball bearing is rotated at a high speed, the column portion 104b opens to the outer diameter side with the annular portion 104a of the crown-shaped cage 104 as a torsion shaft by centrifugal force, so that the spherical pocket of the crown-shaped cage 104 The contact surface pressure between the inner diameter side of 104c and the ball 103 increases, and there arises a problem that the inner diameter side of the pocket 104c wears and heat generation increases.

  Further, as the wear on the inner diameter side of the pocket 104c progresses, the swing of the crown-shaped cage 104 increases, the outer diameter side of the crown-shaped cage 104 and the inner peripheral surface of the outer ring 102 come into contact, and the column portion 104b There is also the problem of wear and in the worst case it breaks.

  To solve such a problem, it is necessary to improve the lubrication state between the inner diameter side of the pocket and the ball, but when the bearing rotates, the lubricating oil also receives centrifugal force and tries to flow on the outer diameter side. Some measures are required.

For example, in Patent Document 1, as shown in FIG. 16, the pocket opening side (opposite side to the annular portion) of the crown-shaped cage 104 is directed to the supply side of the lubricating oil 100, and the seal member 105 is provided on the opposite side. Thus, the lubricating oil 100 is directly attached to the balls 103.
JP 2007-177858 A

  However, in the deep groove ball bearing as shown in FIG. 16, when the lubricating oil 100 is forcibly supplied from one side, if the seal member 105 exists on the opposite side (lubricating oil discharge side), the lubricating oil 100 penetrates. This leads to an increase in the load on the lubricating oil pump. Further, when the annular portion 104a of the crown-shaped cage 104 is on the seal member 105 side, the annular portion 104a of the cage 104 rotates in the lubricating oil 100 accumulated between the seal member 105 and the ball 103. As a result, the agitation resistance increases, which may increase torque.

  Further, since the supplied lubricating oil 100 is blown to the bearing outer diameter side by centrifugal force, the lubricating oil 100 does not reach the tip 104p side (particularly the inner diameter side) of the column portion 104b of the crown retainer 104, and the crown retainer There is a risk of causing wear or seizure at the sliding portion of 104 and ball 103. Since this problem becomes more prominent as the bearing speed increases, it must be said that it is difficult to actually increase the speed.

  In particular, as shown in FIGS. 17 and 18, the tip 104 p of the column portion 104 b of the crown-shaped cage 104 has a snapping force that prevents the cage 104 from falling out when the crown-shaped cage 104 rattles in the axial direction. This is a portion that is pressed against the ball 103 and is very easy to wear. Lack of lubrication to this portion is an obstacle to speeding up.

  The present invention has been made in view of the circumstances described above, and its purpose is to improve the oil film holding performance between the ball and the cage, and to promote appropriate inflow / discharge of the lubricating oil, An object of the present invention is to provide a rolling bearing capable of increasing the allowable rotational speed of the bearing while avoiding the temperature rise of the bearing.

In order to achieve the above-described object, the deep groove ball bearing according to the present invention is characterized by the following (1) to ( 4 ).
(1) An inner ring having an inner ring raceway groove on an outer peripheral surface, an outer ring having an outer ring raceway groove on an inner peripheral surface, and a plurality of balls disposed so as to be freely rollable between the outer ring raceway groove and the inner ring raceway groove; An annular portion and a plurality of pillar portions projecting from one axial end face of the annular portion, and the balls are arranged in a circle by accommodating the balls in pockets formed between the pillar portions. An environment in which lubricating oil is supplied to the ball from one side in the axial direction and discharged from the other side in the axial direction with respect to the ball. In deep groove ball bearings used below,
The annular portion of the crown-shaped cage is disposed toward the one side in the axial direction,
An oil reservoir plate extending toward the shoulder of the inner ring in a state of being fixed to the outer ring side only on the other side in the axial direction, and
Between the inner diameter part of the oil reservoir plate and the outer diameter part of the inner ring, an annular opening for discharging lubricating oil is formed ,
The inner diameter of the oil reservoir plate is equal to or smaller than the inner diameter of the crown-type cage, and the shortest distance between the outer diameter portion of the inner ring forming the annular opening and the inner diameter portion of the oil reservoir plate is 11% or more of the diameter,
The axial shortest distance between the oil reservoir plate and the ball is not more than half of the shortest distance between the ball and the end face of the outer ring,
The deep groove ball bearing characterized in that the annular plate portion of the oil reservoir plate has a curved cross-sectional shape along the outer diameter of the ball.
(2) the inner ring shoulder portion of the axial other side, the outer diameter of the end face portion closer than the outer diameter of the raceway groove near portion, characterized in that it is formed to be smaller according to (1) Deep groove ball bearing.
(3) to the shoulder portion of the inner ring of the axial other side is characterized by a step so that the outer diameter decreases in the end surface inner portion is provided than the outer diameter of the raceway groove inner portion (2 ) Deep groove ball bearing.
(4) the said inner ring shoulder of the axial direction other side is characterized by tapered so that the outer diameter decreases in the end surface inner portion is provided than the outer diameter of the raceway groove inner portion (2 ) Deep groove ball bearing.

  According to the deep groove ball bearing configured as described above, since the oil reservoir plate is arranged on the other side in the axial direction from which the lubricating oil is discharged, the lubricant oil is accumulated in the space between the oil reservoir plate and the ball, It becomes a state close to a so-called oil bath. In addition, since the annular portion of the resin-made crown cage is directed to one side in the axial direction to which the lubricating oil is supplied, the stirring resistance due to the lubricating oil accumulated in the space between the oil reservoir plate and the ball Is suppressed, and the lubricating oil easily adheres to the balls. Therefore, the lubrication state between the pocket and the ball of the crown type cage is improved, and wear of the crown type cage during high-speed rotation can be suppressed. In particular, since the portion on the inner diameter side at the tip of the pillar portion of the crown type cage can be brought into an oil bath state by the oil reservoir effect of the oil reservoir plate, wear of the portion can be suppressed. In addition, since the annular part of the crown type cage is on the side opposite to the side where the lubricating oil is stored, there is a risk that the lubricating oil at the bottom of the pocket will be insufficient. There is no.

In addition, since an annular opening serving as a lubricating oil discharge port is secured between the inner diameter portion of the oil reservoir plate and the outer diameter portion of the inner ring, the lubricating oil can easily pass through the bearing, and the lubricating pump The increase in load can be suppressed. Further, since the oil penetration is improved, the temperature rise of the bearing can be suppressed, the deformation and wear of the crown type cage can be prevented, and the durability life can be improved.
Further, in this deep groove ball bearing, since the oil reservoir plate is provided only on one side, the cost can be reduced as compared with the case where it is provided on both sides.

Further, since the shortest distance between the outer diameter part of the inner ring and the inner diameter part of the oil reservoir plate is 11 % or more of the diameter of the ball, the oil penetration is improved, so that an increase in the load on the lubrication pump can be suppressed, and the bearing Temperature rise can be suppressed.

  In addition, since the inner diameter of the oil reservoir plate is less than the inner diameter of the cage, the lubricating oil blocked by the oil reservoir plate adheres to the pocket inner diameter side where the contact surface pressure with the ball increases during high-speed rotation. It becomes easy and lubrication performance improves.

  Also, by making the shortest axial distance between the oil reservoir plate and the ball less than half the shortest distance between the ball and the end face of the outer ring, the space volume between the ball and the oil reservoir plate can be reduced. Even if it is less, the lubricating oil is likely to accumulate between the ball and the oil reservoir plate, and the lubricating oil is more likely to adhere to the ball.

  In addition, the shoulder portion of the inner ring on the other side in the axial direction is formed so that the outer diameter of the portion closer to the end surface is smaller than the outer diameter of the portion closer to the raceway groove. The inner diameter of the oil reservoir plate can be reduced while ensuring a large size. As a result, the lubricating oil blocked by the oil reservoir plate is likely to adhere to the pocket inner diameter side where the contact surface pressure with the ball becomes high during high-speed rotation.

  In addition, since the shoulder portion of the inner ring is provided with a step or taper, the size of the opening formed between the inner diameter portion of the oil reservoir plate and the outer diameter portion of the inner ring can be provided with easy processing.

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

<First Embodiment>
FIG. 1 is a cross-sectional view of an essential part of the deep groove ball bearing of the first embodiment, FIG. 2 is a perspective view of a crown type cage, and FIG. 3 is a perspective view of an oil reservoir plate.

  As shown in FIG. 1, this deep groove ball bearing includes an inner ring 1 having an inner ring raceway groove 1a on the outer peripheral surface, an outer ring 2 having an outer ring raceway groove 2a on the inner peripheral surface, an inner ring raceway groove 1a and an outer ring raceway groove 2a. A plurality of balls (steel balls) 3 that are arranged so as to roll freely between them, a resin crown-shaped cage 4 that holds the balls 3 in the circumferential direction at predetermined intervals, and the shafts of the inner ring 1 and the outer ring 2 And an oil reservoir plate 5 provided on one end face side in the direction.

  As shown in FIG. 2, the crown-shaped cage 4 includes an annular portion 4a, a plurality of pillar portions 4b that protrude from one axial end face of the annular portion 4a and are arranged at a constant interval, and adjacent pillars. Pockets 4c having spherical inner surfaces secured between the portions 4b, and the balls 3 are held in the respective pockets 4c to hold the balls 3 at predetermined intervals in the circumferential direction. .

  As shown in FIG. 1, this deep groove ball bearing is used in an environment in which lubricating oil is supplied from one axial side (arrow A) to the ball 3 and discharged from the other axial side to the ball 3. The annular portion 4a of the crown type retainer 4 is arranged toward one side in the axial direction to which the lubricating oil is supplied, and the oil reservoir plate 5 is arranged on the other side in the axial direction.

  The oil reservoir plate 5 is an annular plate as shown in FIG. 3, and as shown in FIG. 1, an outer peripheral portion 5a is formed in an engaging groove 2b formed on a side shoulder portion of the outer ring raceway groove 2a of the outer ring 2. Is fixed to the outer ring 2 and is engaged with the inner peripheral surface of the outer ring 2 through the stepped part 5b. The annular plate part 5c is located near the shoulder 1b on the side of the inner ring raceway groove 1a of the inner ring 1. It is extended to. An annular opening 10 through which lubricating oil is discharged is secured between the inner diameter portion 5 d of the oil reservoir plate 5 and the outer diameter portion of the shoulder portion 1 b of the inner ring 1.

In this case, the shortest distance y between the outer diameter portion of the shoulder portion 1b of the inner ring 1 forming the annular opening 10 and the inner diameter portion 5d of the oil reservoir 5 is 9% or more of the diameter Dw of the ball 3, more preferably 11 % Or more is set. In this case, the shortest distance y is set so that the inner diameter of the oil reservoir plate 5 is Ds and the outer diameter of the shoulder 1b of the inner ring 1 is D1.
y = (Ds−D1) / 2
It becomes. Further, the inner diameter Ds of the oil reservoir plate 5 is set to be equal to or less than the revolution diameter PCD of the ball 3, and is further set to be equal to or less than the inner diameter Dh of the crown type cage 4. Further, the shortest axial distance Ls between the annular plate portion 5c of the oil reservoir plate 5 and the ball 3 is less than or equal to half the shortest distance Lt between the ball 3 and the end face of the outer ring 2 (in this embodiment, 20% of Lt). Is set.

  According to the deep groove ball bearing having the above-described configuration, the oil reservoir plate 5 is disposed on the other side in the axial direction, which is the side from which the lubricating oil is discharged, and therefore lubrication is performed in the space between the oil reservoir plate 5 and the ball 3. Oil accumulates and the inside of the bearing is close to a so-called oil bath. In addition, since the annular portion 4a of the crown-shaped cage 4 is directed to one axial side that is the side to which the lubricating oil is supplied, the lubricating oil collected in the space between the oil reservoir 5 and the balls 3 Is suppressed, and the lubricating oil easily adheres to the balls 3.

  Therefore, the lubrication state between the pocket 4c of the crown-type cage 4 and the balls 3 is improved, and wear of the crown-type cage 4 during high-speed rotation can be suppressed. In particular, since the portion on the inner diameter side of the tip 4p of the column portion 4b of the crown type retainer 4 can be brought into an oil bath state by the oil reservoir effect by the oil reservoir plate 5, wear of the portion can be suppressed. Since the annular portion 4a of the crown-shaped cage 4 is on the side opposite to the side where the lubricating oil is accumulated, there is a possibility that the lubricating oil at the bottom of the pocket 4c may be insufficient. It is hard to do and there is no problem.

  Further, since an annular opening 10 serving as a lubricating oil discharge port is secured between the inner diameter portion 5d of the oil reservoir 5 and the outer diameter portion of the shoulder portion 1b of the inner ring 1, the lubricating oil is used as a bearing. Can be easily penetrated, and the load increase of the lubrication pump can be suppressed. Further, since the oil penetration is improved, the temperature rise of the bearing can be suppressed, the deformation and wear of the crown type cage 4 can be prevented, and the durability life can be improved. Moreover, in this deep groove ball bearing, since the oil reservoir plate 5 is provided only on one side, the cost can be reduced as compared with the case where it is provided on both sides.

Further, since the shortest distance y between the outer diameter portion of the shoulder portion 1b of the inner ring 1 and the inner diameter portion 5d of the oil reservoir 5 is set to 9% or more, preferably 11% or more of the diameter Dw of the ball 3, oil penetration is achieved. As a result, an increase in the load on the lubrication pump can be suppressed, and an increase in the temperature of the bearing can be suppressed.

  Further, in this deep groove ball bearing, the inner diameter Ds of the oil reservoir 5 is set to be equal to or smaller than the revolution diameter PCD of the ball 3, so that the sliding portion of the ball 3 and the cage 4, particularly the tip of the column portion 4 b of the crown type cage 4 is used. Lubricating oil can be distributed to the inner diameter side portion of the shaft, and seizure of that portion can be effectively prevented, and the allowable rotational speed of the bearing can be increased. Therefore, it is possible to achieve both the performance of storing the lubricating oil by the oil reservoir plate 5 and the oil penetration, and to improve the lubrication state. In particular, since the inner diameter Ds of the oil reservoir plate 5 is equal to or smaller than the inner diameter Dh of the retainer 4, the lubricating oil blocked by the oil reservoir plate 5 increases the contact surface pressure with the ball 3 during high speed rotation. It becomes easy to adhere to the inner diameter side of the pocket 4c, and the lubricating performance is improved.

  Furthermore, in this deep groove ball bearing, the shortest axial distance Ls between the oil reservoir plate 5 and the ball 3 is made less than or equal to half of the shortest distance Lt between the ball 3 and the end face of the outer ring 2, whereby the ball 3 and the oil reservoir plate. Since the space volume between 5 can be reduced, even if the amount of supplied oil is small, the lubricating oil is likely to accumulate between the balls 3 and the oil reservoir plate 5, and the lubricating oil is more likely to adhere to the balls.

Second Embodiment
FIG. 4 is a cross-sectional view of the main part of the deep groove ball bearing of the second embodiment.
In the deep groove ball bearing of the present embodiment, a step 1c is provided on the outer diameter surface of the shoulder portion 1b of the inner ring 1 on the lubricating oil discharge side, so that the shoulder portion 1b of the inner ring 1 is a portion closer to the raceway groove. It is formed so that the outer diameter of the portion closer to the end face is smaller than the outer diameter. The same members as those in the first embodiment shown in FIG.

  By providing the step 1c on the shoulder 1b of the inner ring 1 in this way, it is possible to reduce the inner diameter Ds of the oil reservoir plate 5 while ensuring a large opening 10 serving as a lubricant discharge port. Therefore, the lubricating oil blocked by the oil reservoir plate 5 is likely to adhere to the inner diameter side of the pocket 4c where the contact surface pressure with the ball 3 increases during high speed rotation, and the contact surface pressure with the ball 3 during high speed rotation. Can prevent wear on the inner diameter side of the pocket 4c. In this case, since the outer diameter of the shoulder 1b is changed by providing the step 1c on the shoulder 1b of the inner ring 1, the inner diameter 5d of the oil reservoir 5 and the shoulder 1b of the inner ring 1 can be easily processed. The dimension of the opening 10 formed between the outer diameter portions of the two can be given. Other effects are the same as those of the first embodiment.

<Third Embodiment>
FIG. 5 is a cross-sectional view of the main part of the deep groove ball bearing of the third embodiment.
In the deep groove ball bearing of the present embodiment, a taper 1d is provided on the outer diameter surface of the shoulder 1b of the inner ring 1 on the lubricating oil discharge side, so that the shoulder 1b of the inner ring 1 is a portion closer to the raceway groove. It is formed so that the outer diameter of the portion closer to the end face is smaller than the outer diameter. The same members as those in the first embodiment shown in FIG.

  Thus, by providing the taper 1d on the shoulder 1b of the inner ring 1, the inner diameter Ds of the oil reservoir plate 5 can be reduced while ensuring a large opening 10 serving as a lubricant discharge port. Therefore, the lubricating oil blocked by the oil reservoir plate 5 is likely to adhere to the inner diameter side of the pocket 4c where the contact surface pressure with the ball 3 increases during high speed rotation, and the contact surface pressure with the ball 3 during high speed rotation. Can prevent wear on the inner diameter side of the pocket 4c. In this case, since the outer diameter of the shoulder portion 1b is changed by providing the taper 1d on the shoulder portion 1b of the inner ring 1, the oil reservoir can be obtained simply by changing the axial position of the inner diameter portion 5d of the oil reservoir plate 5. The size of the opening 10 secured between the inner diameter portion 5d of the plate 5 and the shoulder portion of the inner ring 1 can be easily changed. Other effects are the same as those of the first embodiment.

<Fourth embodiment>
FIG. 6 is a cross-sectional view of a main part of the deep groove ball bearing of the fourth embodiment.
In the deep groove ball bearing of this embodiment, the annular plate portion 5 c of the oil reservoir plate 15 is formed in a curved cross-sectional shape along the outer shape of the ball 3. In this case, the lubricating oil blocked by the oil reservoir plate 15 is more likely to adhere to the balls 3 and the pockets 4c of the crown type retainer 4. Other effects are the same as those of the first embodiment.

<Fifth Embodiment>
FIG. 7 is a cross-sectional view of the main part of the deep groove ball bearing of the fifth embodiment.
In the deep groove ball bearing of this embodiment, the step portion of the oil reservoir plate 25 is omitted, the annular plate portion 5c is formed obliquely, that is, in a conical plate shape, and the inner diameter portion 5d that is the inner peripheral end of the annular plate portion 5c is formed. , Close to the ball 3. In this case, an oil reservoir can be secured in the shoulder portion of the outer ring 2, and when the lubricating oil is small, a larger amount of lubricating oil can be stored in the bearing. Other effects are the same as those of the first embodiment.

<Sixth Embodiment>
FIG. 8 is a cross-sectional view of the main part of the deep groove ball bearing of the sixth embodiment.
In the deep groove ball bearing of this embodiment, a slinger is used as the oil reservoir plate 35. The slinger is for protecting the bearing by shaking off rain or dust from the outside. By using this, the engagement groove 2b can be omitted from the outer ring 2. Other effects are the same as those of the first embodiment.

<Seventh embodiment>
FIG. 9 is a cross-sectional view of the main part of the deep groove ball bearing of the seventh embodiment.
In the deep groove ball bearing of this embodiment, the annular plate portion 5c of the oil reservoir plate 45 is formed by bending the outer peripheral portion 5a fitted in the engagement groove 2b of the outer ring 2 in the axial direction without providing the step portion 5b. It is located on the side close to the bearing end face. As described above, when the annular plate portion 5c of the oil reservoir plate 45 is positioned on the side close to the bearing end surface, a large space can be taken between the balls 3 and the oil reservoir plate 45, so that a large amount of lubrication is achieved. Oil can be stored in the space between the ball 3 and the oil reservoir plate 45.

  Further, in this bearing, an annular groove 1e is formed on the outer diameter surface of the shoulder portion 1b of the inner ring 1, and the outer diameter on the bearing end surface side of the annular groove 1e is larger than the outer diameter of the shoulder portion 1b on the inner side of the annular groove 1e. It is set smaller. Then, the inner diameter portion 5d of the oil reservoir plate 45 is opposed to the outer diameter surface closer to the bearing end surface than the annular groove 1e with a gap, and the gap serves as an opening 10 for discharging the lubricating oil. Other configurations are the same as those in the first embodiment, and the same members are denoted by the same reference numerals and description thereof is omitted.

  According to the deep groove ball bearing of this embodiment, since a lot of lubricating oil can be stored inside the bearing as described above, it can be expected that the effects of the first embodiment are more remarkably exhibited.

  In addition, this invention is not limited to embodiment mentioned above, A deformation | transformation, improvement, etc. are possible suitably. In addition, the material, shape, dimensions, 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.

  For example, in each of the embodiments described above, the oil reservoir plates 5, 15, 25, 35, and 45 are directly attached to the shoulders of the outer ring 2, but as shown in FIG. As shown in FIG. 11, an annular plate 56 is sandwiched between the side plate 55a of the housing 55 and the side surface of the outer ring 2, and the annular plate 56 is used as an oil reservoir plate. Also good.

  In the case of the example in FIG. 10, a shield-like oil reservoir need not be specially prepared, and a process such as press-fitting can be omitted, thereby reducing the cost. In the case of the example shown in FIG. 11, it is not necessary to process the housing 55 as an oil reservoir, and unlike the first to seventh embodiments, a simple annular plate 26 is attached to the housing 55. By simply attaching to the side plate 55a, it can function as an oil reservoir plate.

<Test 1>
Next, a run-out test was performed using a deep groove ball bearing having the configuration shown in FIG. 9 (bearing name number 6011: bearing inner diameter = 55 mm, bearing outer diameter = 90 mm, bearing width 18 mm). In this test 1, the deep groove in which y / Dw (gap / ball diameter) was changed by fixing the inner diameter Ds of the oil reservoir plate 45 to 65 mm and changing the outer diameter D1 of the shoulder 1b of the inner ring 1 One ball bearing was prepared one by one, and each was rotated under the following conditions, and the time until the whirling occurred was investigated. The bearing configuration and test conditions are as follows.

<Bearing configuration>
-Cage: Crown type cage with spherical pockets-Cage material: Carbon fiber 15% reinforced 46 nylon-Inner diameter Dh of crown type cage = 67.9 mm
・ Ball revolution diameter PCD = 72.5mm

<Test conditions>
・ Rotation speed: 30000 rpm
・ Oil supply temperature: 120 ℃
Lubrication method: VG24 mineral oil forced lubrication 0.1 (l / min)
・ Load: 3400N
・ Test time: 20Hr, 50Hr, 100Hr, and thereafter TP confirmation every 100Hr

  The results of the run-out test were as shown in Table 1 and FIG.

  According to the run-out test result shown in FIG. 12, when y / Dw is 9% or more, the improvement of the run-out start time of the deep groove ball bearing is almost saturated, and when y / Dw is 11% or more, the run-out start time. It can be seen that the improvement is completely saturated. From this, it was verified that if y / Dw is 9% or more, preferably 11% or more, a great effect can be obtained for reduction of runout.

<Test 2>
In this test 2, y = 1.14 mm (y / Dw = 0.11) is fixed in the deep groove ball bearing (bearing name 6011) of FIG. 9, and the inner diameter Dh of the crown type cage 4 and the oil reservoir plate 45 are fixed. When the difference in the inner diameter Ds was changed (however, the inner diameter Dh (= 68.3 mm) of the crown-shaped cage 4 was fixed), the presence or absence of occurrence of run-out was observed. Test conditions are the same as in Test 1.

  The results of the run-out test were as shown in Table 2 and FIG.

  As can be seen from the graph of FIG. 13, when the inner diameter Ds of the oil reservoir plate 45 exceeds the inner diameter Dh of the crown cage 4 (Dh−Ds is negative), the inner diameter side of the oil reservoir plate 45 is caused by centrifugal force during high-speed rotation. 14, as shown in FIG. 14, the oil bath portion is blown to the outer peripheral side of the bearing, so that an oil bath portion cannot be formed in the sliding portion with the ball 3 on the inner diameter side of the tip 4 p of the column portion 4 b of the crown type cage 4. , The time to swing around is shortened. Therefore, if the inner diameter Ds of the oil reservoir plate 45 is equal to or smaller than the inner diameter Dh of the cage 4, it can be said that the lubricating oil is sufficiently spread between the crown type cage 4 and the balls 3, and the anti-vibration property can be improved. I understand that.

It is principal part sectional drawing of the deep groove ball bearing of 1st Embodiment of this invention. It is a perspective view of the crown type cage used for the bearing. It is a perspective view of the oil reservoir used for the bearing. It is principal part sectional drawing of the deep groove ball bearing of 2nd Embodiment of this invention. It is principal part sectional drawing of the deep groove ball bearing of 3rd Embodiment of this invention. It is principal part sectional drawing of the deep groove ball bearing of 4th Embodiment of this invention. It is principal part sectional drawing of the deep groove ball bearing of 5th Embodiment of this invention. It is principal part sectional drawing of the deep groove ball bearing of 6th Embodiment of this invention. It is principal part sectional drawing of the deep groove ball bearing of 7th Embodiment of this invention. It is principal part sectional drawing for the schematic explanation of other embodiment of this invention. It is principal part sectional drawing for the schematic explanation of other embodiment of this invention. It is a graph which shows the 1st test result which verifies the significance of the numerical limitation in the bearing of 7th Embodiment of this invention. It is a graph which shows the 2nd test result of the bearing. It is sectional drawing shown in order to demonstrate the significance of the numerical limitation of the bearing. It is principal part sectional drawing of the deep groove ball bearing which has the conventional crown type cage. It is principal part sectional drawing of the conventional deep groove ball bearing which has the sealing material on the one side. It is a principal part perspective view which shows the location where the crown type holder | retainer of the said bearing deform | transforms. (A) And (b) is the side view and front view which are shown for description of the problem of the holder | retainer of the same kind.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Inner ring 1a Inner ring raceway groove 1b Shoulder part 2 Outer ring 2a Outer ring raceway groove 3 Ball 4 Crown type retainer 4a Ring part 4b Column part 4c Pocket 4p Tip part 5, 15, 25, 35, 45 Oil reservoir 100 Lubricating oil D1 Inner ring outer diameter Ds Oil reservoir inner diameter Dh Crowned cage inner diameter PCD Ball revolution diameter

Claims (4)

An inner ring having an inner ring raceway groove on an outer peripheral surface, an outer ring having an outer ring raceway groove on an inner peripheral surface, a plurality of balls arranged in a freely rolling manner between the outer ring raceway groove and the inner ring raceway groove; And a plurality of pillars projecting from one end face in the axial direction of the annular part, and the balls are predetermined in the circumferential direction by accommodating the balls in pockets formed between the pillars A crown-shaped cage made of resin that is held at intervals, and is used in an environment in which lubricating oil is supplied from one axial side to the ball and discharged from the other axial side to the ball In deep groove ball bearings,
The annular portion of the crown-shaped cage is disposed toward the one side in the axial direction,
An oil reservoir plate extending toward the shoulder of the inner ring in a state of being fixed to the outer ring side only on the other side in the axial direction, and
Between the inner diameter part of the oil reservoir plate and the outer diameter part of the inner ring, an annular opening for discharging lubricating oil is formed ,
The inner diameter of the oil reservoir plate is equal to or smaller than the inner diameter of the crown-type cage, and the shortest distance between the outer diameter portion of the inner ring forming the annular opening and the inner diameter portion of the oil reservoir plate is 11% or more of the diameter,
The axial shortest distance between the oil reservoir plate and the ball is not more than half of the shortest distance between the ball and the end face of the outer ring,
The deep groove ball bearing characterized in that the annular plate portion of the oil reservoir plate has a curved cross-sectional shape along the outer diameter of the ball. 2. The deep groove ball bearing according to claim 1 , wherein a shoulder portion of the inner ring on the other side in the axial direction is formed so that an outer diameter of a portion near the end surface is smaller than an outer diameter of the portion near the raceway groove. . The inner ring shoulder portion of the axial other side, according to claim 2, characterized in that the step is provided so that the outer diameter of the end face portion closer than the outer diameter of the raceway groove inner portion is reduced Deep groove ball bearing. The inner ring shoulder portion of the axial other side, according to claim 2, characterized in that the taper is provided so that the outer diameter of the end face portion closer than the outer diameter of the raceway groove inner portion is reduced Deep groove ball bearing.

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