JP2018066396A - Rolling bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rolling bearing which can inhibit grease filling an annular space between an inner ring and an outer ring from leaking to the outside through a labyrinth gap between the inner ring and non-contact seals.SOLUTION: A rolling bearing includes: an inner ring 3; an outer ring 2; balls 4; a holder 5; and a pair of seals 6, 7 which are provided at both axial end parts of an annular space S between the inner ring 3 and the outer ring 2. The seals 6, 7 are non-contact seals which are fixed to the outer ring 2 and form labyrinth gaps 45, 55 with the inner ring 3. An outer peripheral surface 32a of a second inner shoulder part 32 of the inner ring 3 is used as a guide surface which guides rotation of the holder 5.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a rolling bearing.

  Rolling bearings are known as bearings that support the rotating shafts of various mechanical devices, and the rolling bearings require reliability such that seizure does not occur. Accordingly, rolling bearings employing grease lubrication having high lubrication performance are increasing even in the case of high-speed rotation applications. In this grease lubrication, the bearing is filled with grease in advance (see, for example, Patent Document 1).

  FIG. 5 is a cross-sectional view showing an example of a conventional rolling bearing. The rolling bearing 90 is an angular ball bearing, and includes an inner ring 91, an outer ring 92, a plurality of balls 93, and an annular cage 94. The plurality of balls 93 are in contact with the inner ring 91 and the outer ring 92 at a predetermined angle (contact angle), and are held by the retainer 94 at intervals in the circumferential direction. The retainer 94 is guided (positioned) by its outer peripheral surface being in surface contact with the inner peripheral surface of the outer ring 92.

  As described above, in the bearing in which grease is filled in the bearing, that is, in the annular space 95 formed between the inner ring 91 and the outer ring 92, the seals 96 and 97 are provided on both sides in the axial direction of the annular space 95. It has been. In the rolling bearing 90 shown in FIG. 5, the seals 96 and 97 are labyrinth seals (non-contact seals) in order to realize high-speed rotation. That is, the labyrinth gaps 96a and 97a are formed between the seals 96 and 97 and the inner ring 91, thereby preventing the grease from flowing out.

JP, 2015-203474, A

  In the rolling bearing 90, since the outer peripheral surface of the cage 94 is guided in surface contact with the inner peripheral surface of the outer ring 92, a large space 98 is formed between the inner peripheral surface of the cage 94 and the outer peripheral surface of the inner ring 91. It is formed. For this reason, grease tends to stay on the outer peripheral surface of the inner ring 91, and the staying grease may enter the labyrinth gaps 96a and 97a and leak to the outside of the bearing. When grease leaks, lubrication failure occurs in the rolling bearing 90, and problems such as seizure, temperature rise, and wear may occur.

  Accordingly, the present invention provides a rolling bearing capable of suppressing the grease filled in the annular space between the inner ring and the outer ring from leaking outside through the labyrinth gap between the inner ring and the non-contact seal. The purpose is to do.

  The present invention provides an inner ring, an outer ring, a plurality of rolling elements provided between the inner ring and the outer ring, an annular cage for holding the rolling element, and an annular space between the inner ring and the outer ring. A non-contact seal provided with a pair of seals provided at both axial ends of the annular space to prevent the grease from flowing out, the seal being fixed to the outer ring and forming a labyrinth gap with the inner ring In the rolling bearing, at least a part of the outer peripheral surface of the inner ring is a guide surface that guides the rotation of the cage.

  According to the present invention, since at least a part of the outer peripheral surface of the inner ring is a guide surface that guides the rotation of the cage, the inner peripheral surface of the outer ring is used as the guide surface of the cage as in the prior art. As compared with the above, the space between the inner peripheral surface of the cage and the outer peripheral surface (guide surface) of the inner ring can be reduced. As a result, the amount of grease that stays in the space between the inner peripheral surface of the cage and the guide surface of the inner ring is reduced, so that the grease is prevented from leaking outside through the labyrinth gap between the inner ring and the non-contact seal. can do.

The inner ring has a first shoulder formed on one axial side and a second shoulder having an outer diameter smaller than the outer diameter of the first shoulder formed on the other axial side. The outer peripheral surface of the second shoulder is preferably the guide surface.
In this case, the space between the outer peripheral surface of the second shoulder portion of the inner ring and the inner peripheral surface of the cage can be reduced. Thereby, since the amount of grease staying in the space is reduced, it is possible to prevent the grease from leaking to the outside through the labyrinth gap between the non-contact seal on the second flange side and the inner ring. Particularly effective when grease is more likely to leak from the labyrinth gap between the non-contact seal on the second shoulder side and the inner ring than the labyrinth gap between the non-contact seal on the first shoulder side and the inner ring. Become.

The retainer preferably includes a guided surface that is slidably opposed to the guide surface, and a tapered surface that gradually increases in diameter from the guided surface toward one side in the axial direction.
In this case, excess grease existing in the space between the guide surface of the inner ring and the guided surface of the cage is transferred from the guided surface of the cage to the tapered surface due to the centrifugal force accompanying the rotation of the cage, and the diameter is reduced. It becomes easy to flow toward the outer ring on the outer side in the direction. Accordingly, the amount of grease staying in the space can be further reduced, and the lubricity between the outer ring and the rolling element can be improved.

  Moreover, it is preferable that the chamfered part is formed in the inner peripheral edge of the said other axial direction side of the said holder. In this case, a predetermined gap can be secured between the chamfered portion of the cage and the inner ring side end portion of the non-contact seal on the other axial side, so that the guide surface of the inner ring and the inner circumferential surface of the cage The excess grease existing in the space between the two parts easily flows from the inner peripheral surface of the cage through the chamfered portion toward the outer ring in the radial direction by the centrifugal force accompanying the rotation of the cage. As a result, the amount of grease staying in the space can be further reduced, and the lubricity between the outer ring and the rolling element can be further improved.

  Further, the labyrinth gap between the non-contact seal on the other axial side and the inner ring is formed so that the grease can easily enter than the labyrinth gap between the non-contact seal on the one axial side and the inner ring. In this case, the grease is more likely to enter the labyrinth gap on the other side in the axial direction than the labyrinth gap on the one side in the axial direction. For this reason, as described above, the outer peripheral surface of the second shoulder portion on the other side in the axial direction is used as the guide surface, thereby effectively preventing grease from leaking to the outside from the labyrinth gap on the other side in the axial direction. be able to.

  The path length of the labyrinth gap between the non-contact seal on the other side in the axial direction and the inner ring is shorter than the path length of the labyrinth gap between the non-contact seal on the one side in the axial direction and the inner ring. The grease is more likely to leak from the labyrinth gap on the other side in the axial direction than the labyrinth gap on the one side in the axial direction. For this reason, as described above, the outer peripheral surface of the second shoulder portion on the one axial side is used as the guide surface, thereby effectively preventing grease from leaking to the outside from the labyrinth gap on the one axial side. be able to.

In addition, the retainer includes an annular portion disposed on the second shoulder side, and a plurality of pillar portions provided extending from the annular portion to the first shoulder side. preferable.
In this case, the space between the outer peripheral surface of the second shoulder portion of the inner ring and the inner peripheral surface of the annular portion of the cage can be reduced. Thereby, since the amount of grease staying in the space is reduced, it is possible to prevent the grease from leaking outside from the labyrinth gap between the non-contact seal on the second shoulder side and the inner ring.

  According to the present invention, it is possible to prevent the grease filled in the annular space between the inner ring and the outer ring from leaking outside through the labyrinth gap between the inner ring and the non-contact seal.

It is a longitudinal section showing a rolling bearing concerning one embodiment of the present invention. It is an expanded sectional view of the 1st seal and the 1st seal groove. It is an expanded sectional view of the 2nd seal and the 2nd seal groove. It is a longitudinal cross-sectional view which shows the modification of a holder | retainer. It is sectional drawing which shows an example of the conventional rolling bearing.

Hereinafter, an embodiment of the rolling bearing of the present invention will be described.
[Overall configuration of rolling bearing]
FIG. 1 is a longitudinal sectional view showing a rolling bearing according to an embodiment of the present invention. The rolling bearing of the present embodiment is an angular ball bearing 1, and includes an outer ring 2, an inner ring 3, a plurality of balls (rolling elements) 4, an annular cage 5, a first seal 6, and a second seal 7. And. The annular space S formed between the outer ring 2 and the inner ring 3 is filled with grease. In other words, the angular ball bearing 1 employs grease lubrication, and ensures lubrication performance. In this embodiment, the angular ball bearing 1 is used under the condition of high speed rotation.
In the following description, the terms “one side in the axial direction” and “the other side in the axial direction” are used with respect to the position in the axial direction. One side in the axial direction is the right side in FIG. 1, and the other side in the axial direction is the left side in FIG.

  An outer ring raceway groove 20 on which the balls 4 roll is formed on the inner peripheral surface of the outer ring 2. The ball 4 comes into contact with the outer ring raceway groove 20 at a predetermined contact angle. The outer ring 2 has a first outer shoulder portion 21 and a second outer shoulder portion 22 on both sides in the axial direction with the outer ring raceway groove 20 in between. In this embodiment, the inner diameter (shoulder diameter) ) Is smaller than the inner diameter (shoulder diameter) of the first outer shoulder 21. In addition, a first groove 24 for fixing the first seal 6 is formed at the end of the first outer shoulder 21 on the one axial side, and the second outer shoulder 22 on the other side in the axial direction is formed. A second groove 25 for fixing the second seal 7 is formed at the end.

  An inner ring raceway groove 30 on which the balls 4 roll is formed on the outer circumferential surface of the inner ring 3. The ball 4 contacts the inner ring raceway groove 30 at a predetermined contact angle. The inner ring 3 has a first inner shoulder part (first shoulder part) 31 and a second inner shoulder part (second shoulder part) 32 on both sides in the axial direction across the inner ring raceway groove 30. The outer diameter (shoulder diameter) of the second inner shoulder portion 32 is smaller than the outer diameter (shoulder diameter) of the first inner shoulder portion 31. Further, a first seal groove 34 is formed at an end portion on the one axial side of the first inner shoulder portion 31, and a second seal is formed at an end portion on the other axial side of the second inner shoulder portion 32. A groove 35 is formed. Thus, the outer peripheral surface of the inner ring 3 has a shape in which the outer diameter gradually decreases from one side in the axial direction toward the other side (excluding the formation region of the seal grooves 34 and 35) as a whole. A shape having a different shoulder diameter on one side and the other side in the axial direction as in the present embodiment is hereinafter referred to as an angular shape.

  The plurality of balls 4 are provided in an annular space S between the outer ring 2 and the inner ring 3, and when the angular ball bearing 1 rotates (in this embodiment, the inner ring 3 rotates), these balls 4 are held in a cage. 5, the outer ring raceway groove 20 and the inner ring raceway groove 30 are rolled.

  The cage 5 can hold a plurality of balls 4 at predetermined intervals (equal intervals) along the circumferential direction. For this purpose, the cage 5 has pockets 10 for accommodating the balls 4. A plurality are formed along the circumferential direction. The cage 5 of the present embodiment is a so-called crown-shaped cage, and an annular portion 11 disposed on the other axial side (second outer shoulder portion 22 side) of the ball 4 and the annular portion. 11 and a plurality of pillars 12 provided extending in the axial direction on one side (first outer shoulder 21 side), and a pocket 10 is formed between a pair of pillars 12 and 12 adjacent in the circumferential direction. It becomes. The cage 5 of the present embodiment is made of resin, but may be made of metal.

  The first seal 6 includes an annular cored bar 41 and a seal body 42 fixed to the cored bar 41. The core metal 41 is made of metal, the seal body 42 is made of rubber, and the seal body 42 is fixed to the core metal 41. The seal body 42 includes a radially outer end 43 attached to the first groove 24 and a lip portion (first lip portion) 44 that faces the first seal groove 34 with a gap. . The first seal 6 is attached to the outer ring 2 by the radial outer end 43 being fitted and fixed in the first groove 24. A slight gap is formed between the first lip portion 44 and the first seal groove 34, and this gap becomes a labyrinth gap (first labyrinth gap) 45. That is, the labyrinth seal (non-contact seal) is configured by the first lip portion 44 and the first seal groove 34.

  The second seal 7 includes an annular cored bar 51 and a seal body 52 fixed to the cored bar 51. The core metal 51 is made of metal, the seal body 52 is made of rubber, and the seal body 52 is fixed to the core metal 51. The seal body 52 has a radially outer end 53 attached to the second groove 25 and a lip portion (second lip portion) 54 facing the second seal groove 35 with a gap. . The second seal 7 is attached to the outer ring 2 by the radial outer end 53 being fitted and fixed in the second groove 25. A slight gap is formed between the second lip portion 54 and the second seal groove 35, and this gap becomes a labyrinth gap (second labyrinth gap) 55. That is, the second lip portion 54 and the second seal groove 35 constitute a labyrinth seal (non-contact seal). Thus, it becomes a structure suitable for high-speed rotation by setting it as a non-contact seal.

  As described above, the angular ball bearing 1 shown in FIG. 1 includes the first seal 6 having the first lip portion 44 and the second seal 7 having the second lip portion 54. The first seal 6 is provided on one side of the annular space S in the axial direction, and forms a first labyrinth gap 45 between the inner ring 3 and prevents the grease from flowing out. The second seal 7 is provided on the other axial side of the annular space S, and a second labyrinth gap 55 is formed between the second seal 7 and the inner ring 3 to prevent the grease from flowing out. The seals 6 and 7 prevent the grease existing in the annular space S from leaking to the outside.

[About the first seal 6 and the second seal 7]
FIG. 2 is an enlarged cross-sectional view of the first seal 6 and the first seal groove 34. The first lip portion 44 of the first seal 6 has a main body portion 44a that is partly fixed to the core metal 41, and a protruding portion 44b that protrudes radially inward from the inner peripheral side of the main body portion 44a. doing. And both the main-body part 44a and the protrusion part 44b are the states accommodated in the 1st seal groove 34. FIG.

The first lip portion 44 has a lip inclined surface 60 that faces the annular space S. The lip inclined surface 60 is formed to extend outward in the radial direction from the end on the other axial side of the main body 44a toward the one axial side.
Further, the first lip portion 44 has a lip side surface 61, a lip inner cylindrical surface 62, a lip annular surface 63, a lip middle cylindrical surface 64, a lip as a surface facing the inner ring 3 in this order from the bearing inner side (ball 4 side). It has an intermediate slope 65 and an outer lip cylindrical surface 66. In contrast, the first seal groove 34 has, in order from the bearing inner side (ball 4 side), an inner annular side surface 34a, an inner cylindrical surface 34b, an intermediate annular side surface 34c, an intermediate cylindrical surface 34d, and a raised convex surface 34e. ing.

  The lip side surface 61 faces the inner annular side surface 34a, the lip inner cylindrical surface 62 faces the inner cylindrical surface 34b, the lip annular surface 63 faces the middle annular side surface 34c, and the lip middle cylindrical surface 64 is the middle cylindrical surface. The lip middle slope 65 and the lip outer cylindrical surface 66 are opposed to the raised convex surface 34e. A first labyrinth gap 45 is formed between these opposing surfaces. Further, the gap between the lip side surface 61 and the inner annular side surface 34a is the inlet portion 45a side of the first labyrinth gap 45, and the gap between the lip outer cylindrical surface 66 and the raised convex surface 34e is the outlet portion 45b of the first labyrinth gap 45. On the side.

  FIG. 3 is an enlarged cross-sectional view of the second seal 7 and the second seal groove 35. The second lip portion 54 of the second seal 7 has a main body portion 54a partially fixed to the core metal 51, and a protruding portion 54b protruding radially inward from the inner peripheral side of the main body portion 54a. doing. Only the protrusion 54 b is accommodated in the second seal groove 35.

The second lip portion 54 has a lip inclined surface 70 facing the annular space S. The lip inclined surface 60 is formed so as to extend radially outward from the end on one side in the axial direction of the main body 54a toward the other side in the axial direction.
Further, the second lip portion 54 is a surface facing the inner ring 3 in order from the bearing inner side (the ball 4 side) in order from the lip inner cylindrical surface 71, the lip annular surface 72, the lip middle cylindrical surface 73, the lip middle slope 74, And a lip outer cylindrical surface 75. On the other hand, the second seal groove 35 has an annular side surface 35a, a cylindrical surface 35b, and a raised convex surface 35c in order from the bearing inner side (the ball 4 side).

  The lip inner cylindrical surface 71 faces a part of the outer peripheral surface 32 a of the second inner shoulder portion 32. The lip annular surface 72 faces the annular side surface 35a, the lip middle cylindrical surface 73 faces the cylindrical surface 35b, and the lip middle slope 74 and the lip outer cylindrical surface 75 face the raised convex surface 35c. A second labyrinth gap 55 is formed between these opposing surfaces. Further, the space between the inner lip inner cylindrical surface 71 and a part of the outer peripheral surface 32a of the second inner shoulder 32 is the inlet 55a side of the second labyrinth gap 55, and the space between the outer cylindrical surface 75 and the raised convex surface 35c. The second labyrinth gap 55 is on the outlet 55b side.

In addition, regarding the surface facing the inner ring 3 included in the first lip portion 44 and the second lip portion 54 of the present embodiment, the surface including the term “cylindrical surface” is a center line that coincides with the center line of the angular ball bearing 1. The surface including the term “annular surface” and the lip side surface 61 are surfaces on an imaginary surface orthogonal to the center line of the angular ball bearing 1.
With respect to the surfaces of the first seal groove 34 and the second seal groove 35 of this embodiment, the surface including the term “annular side surface” is a surface on a virtual surface orthogonal to the center line of the angular ball bearing 1. The surface including the term “cylindrical surface” is a cylindrical surface having a center line coinciding with the center line of the angular ball bearing 1.

In FIG. 2, the axial dimension L1 of the first lip portion 44 is the sum of the axial lengths of the lip inner cylindrical surface 62, the lip inner cylindrical surface 64, the lip inner inclined surface 65, and the lip outer cylindrical surface 66.
In FIG. 3, the axial dimension L2 of the second lip portion 54 is the sum of the axial lengths of the inner lip cylinder surface 71, the inner lip cylinder surface 73, the inner lip slope 74, and the outer lip cylinder surface 75.

The axial lengths of the lip middle cylindrical surface 64, the lip middle slope 65, and the lip outer cylindrical surface 66 of the first lip portion 44 (see FIG. 2) are respectively in the lip middle cylinder of the second lip portion 54 (see FIG. 3). The length in the axial direction of the surface 73, the middle lip surface 74, and the outer cylindrical surface 75 of the lip is the same, but the in-lip cylindrical surface 71 of the second lip portion 54 (see FIG. 3) is the first lip portion 44 (see FIG. 2). ) In the lip inner cylindrical surface 62.
For this reason, the axial dimension L2 of the second lip part 54 is smaller than the axial dimension L1 of the first lip part 44 (L1> L2), and thereby, the first lip part 44 is longer than the path length of the first labyrinth gap 45. The path length of the two labyrinth gap 55 is short.

Further, the first labyrinth gap 45 (see FIG. 2) also includes a small space between the inner annular side face 34a and the lip side face 61 facing in the axial direction on the inlet 45a side of the first labyrinth gap 45. included.
On the other hand, the second labyrinth gap 55 (see FIG. 3) is a surface facing the radial direction on the inlet portion 55a side of the second labyrinth gap 55 (inner lip cylindrical surface 71 and outer peripheral surface 32a). However, there is no surface facing in the axial direction.

  That is, in the present embodiment (see FIG. 2), the inner ring 3 has an inner annular side surface 34a that is provided radially inward from the outer peripheral surface 31a of the first inner shoulder portion 31. The 1 lip portion 44 has a lip side surface 61 facing the inner annular side surface 34a with a gap. Since the gap (small space) between the inner annular side surface 34 a and the lip side surface 61 is also included in the first labyrinth gap 45, the second labyrinth is longer than the path length of the first labyrinth gap 45. The path length of the gap 55 is shortened.

Further, in the first seal 6 of the present embodiment (see FIG. 2), an inlet 45a of the first labyrinth gap 45 is formed between the inner annular side surface 34a and the lip side surface 61 facing in the axial direction. Yes. And this entrance part 45a is opening toward radial direction outer side.
On the other hand, in the second seal 7 of the present embodiment (see FIG. 3), the inlet portion 55a of the second labyrinth gap 55 is formed between the lip inner cylindrical surface 71 and the outer peripheral surface 32a facing each other in the radial direction. ing. And this inlet part 55a is opened toward the one side of the axial direction.

For this reason, in the case of the second seal 7, the grease flowing along the outer peripheral surface 32 a of the second inner shoulder portion 32 among the grease flowing from the one side in the axial direction in the annular space S is the second labyrinth gap 55. It is relatively easy to enter.
On the other hand, in the case of the first seal 6 shown in FIG. 2, the inlet portion 45a of the first labyrinth gap 45 opens toward the radially outer side. The grease that flows along the outer peripheral surface 31 a of the first inner shoulder 31 is less likely to enter the first labyrinth gap 45. Accordingly, the second labyrinth gap 55 is formed more easily than the first labyrinth gap 45 so that the grease can enter.

[Rotation guide of cage 5]
In FIG. 3, the cage 5 of the present embodiment is positioned in the radial direction and rotated and guided by the annular portion 11 being in sliding contact with a part of the inner ring 3 (the outer peripheral surface 32 a of the second inner shoulder portion 32). The inner ring guide retainer. Therefore, the outer peripheral surface 32a of the second inner shoulder portion 32 is a guide surface that guides the rotation of the cage 5, and the inner peripheral surface of the annular portion 11 of the cage 5 can slide on the guide surface 32a. It is set as the guided surface 13 which opposes.

  As a result, the space K between the guide surface 32a of the second shoulder 32 and the guided surface 13 of the cage 5 is separated from the outer circumferential surface of the inner ring 91 and the inner circumferential surface of the cage 94 in the conventional example shown in FIG. It can be made smaller than the space 98 between. As a result, since the amount of grease staying in the space K is reduced, it is possible to suppress the leakage of grease from the second labyrinth gap 55 between the inner ring 3 and the second seal 7 to the outside.

  In particular, in the present embodiment, as described above, the path length of the second labyrinth gap 55 on the other axial side is shorter than the path length of the first labyrinth gap 45 on one axial side (see FIG. 2), and the grease Is easier to enter the inlet portion 55 a of the second labyrinth gap 55 than the inlet portion 45 a of the first labyrinth gap 45. For this reason, the grease is likely to leak to the outside from the second labyrinth gap 55 on the other axial side than the first labyrinth gap 45 on the one axial side, and as described above, the second shoulder portion on the other axial side By using the outer peripheral surface 32a of 32 as the guide surface of the cage 5, it is possible to effectively suppress the leakage of grease from the second labyrinth gap 55 to the outside.

[About shape of cage 5]
In FIG. 1, the guided surface 13, the tapered surface 14, and the inner cylindrical surface 15 are formed in order from the other axial side on the inner periphery of the cage 5 of the present embodiment. In addition, regarding the surface of the inner periphery of the cage 5 of the present embodiment, the surface including the term “cylindrical surface” is a cylindrical surface having a center line coinciding with the center line of the angular ball bearing 1.

  The tapered surface 14 is inclined so as to gradually increase in diameter from the guided surface 13 toward one side in the axial direction, and from the end portion on the one axial side of the inner peripheral surface of the annular portion 11, It is continuously formed over the axially intermediate portion of the inner peripheral surface (see also FIG. 3). The inner cylindrical surface 15 is formed to extend in parallel with the guided surface 13 from the tapered surface 14 toward one side in the axial direction on the inner peripheral surface of the column portion 12.

As a result, when surplus grease exists in the space K, the surplus grease travels from the guided surface 13 of the cage 5 to the tapered surface 14 and the inner cylindrical surface 15 by the centrifugal force accompanying the rotation of the cage 5. Thus, it becomes easier to flow toward the outer ring 2 on the radially outer side. Thereby, since the excess grease can be supplied to the outer ring raceway groove 20, the amount of grease staying in the space K can be further reduced, and the lubricity of the outer ring raceway groove 20 can be improved.

As a result, the amount of grease staying in the space K can be further reduced, so that the leakage of grease from the second labyrinth gap 55 between the inner ring 3 and the second seal 7 can be further suppressed. it can.

  An outer cylindrical surface 16, a tapered surface 17, and an inner cylindrical surface 18 are formed on the outer periphery of the cage 5 in this order from the other axial side. In addition, regarding the surface which the outer periphery of the cage 5 of the present embodiment has, the surface including the term “cylindrical surface” is a cylindrical surface having a center line coinciding with the center line of the angular ball bearing 1.

  The outer cylindrical surface 16 is formed in parallel with the guided surface 13 on the outer peripheral surface of the annular portion 11. The taper surface 17 is inclined so as to gradually increase in diameter from the outer cylindrical surface 16 toward one side in the axial direction, and from the end on one side in the axial direction of the outer peripheral surface of the annular portion 11 to the outer periphery of the column portion 12. It is continuously formed over the axial middle part of the surface (see also FIG. 3). The inner cylindrical surface 18 is formed on the outer peripheral surface of the column portion 12 so as to extend in parallel with the outer cylindrical surface 16 from the tapered surface 17 toward one side in the axial direction.

  In FIG. 3, a chamfered portion 19 is formed in the annular portion 11 of the cage 5 at the inner peripheral end edge on the other side in the axial direction. The chamfered portion 19 is inclined so as to gradually increase in diameter from the guided surface 13 toward the other side in the axial direction, and is formed substantially parallel to the lip inclined surface 70 of the second lip portion 54. Thereby, a predetermined gap is secured between the annular portion 11 and the second lip portion 54.

  Therefore, when surplus grease exists in the space K, the surplus grease is transmitted from the guided surface 13 of the cage 5 to the chamfered portion 19 by the centrifugal force accompanying the rotation of the cage 5, and the outer ring on the radially outer side. It becomes easy to flow toward 2. As a result, the excess grease can be supplied to the outer ring raceway groove 20, so that the amount of grease staying in the space K can be further reduced and the lubricity of the outer ring raceway groove 20 can be further improved. .

[Modified example of cage 5]
FIG. 4 is a longitudinal sectional view showing a modified example of the cage 5. In this modification, the tapered surface 14 on the inner periphery of the cage 5 is formed continuously from the end on the one axial side of the inner peripheral surface of the annular portion 11 over the entire inner peripheral surface of the column portion 12. Yes. Therefore, in this modification, only the tapered surface 14 is formed on one side in the axial direction from the guided surface 13 on the inner periphery of the cage 5.
A cylindrical surface 5 a is formed on the outer periphery of the cage 5 over the entire outer peripheral surface of the annular portion 11 and the entire outer peripheral surface of the column portion 12. Therefore, in this modification, only the cylindrical surface 5 a is formed on the outer periphery of the cage 5.

  As described above, also in this modification, when surplus grease exists in the space K, the surplus grease travels from the guided surface 13 of the cage 5 to the tapered surface 14 due to the centrifugal force accompanying the rotation of the cage 5. Thus, it becomes easier to flow toward the outer ring 2 on the radially outer side. Thereby, since the excess grease can be supplied to the outer ring raceway groove 20, the amount of grease staying in the space K can be further reduced, and the lubricity of the outer ring raceway groove 20 can be improved.

  The embodiments disclosed above are illustrative in all respects and not restrictive. That is, the rolling bearing of the present invention is not limited to the illustrated form, but may be of another form within the scope of the present invention. For example, in the above-described embodiment, the case where the rolling bearing 1 is an angular ball bearing has been described. However, the type of the bearing is not limited thereto, and may be another rolling bearing such as a deep groove ball bearing. Moreover, although the said embodiment demonstrated the case where the inner ring | wheel 3 was a rotating wheel, the outer ring | wheel 2 may be a rotating wheel and the inner ring | wheel 3 may be a fixed ring.

  Moreover, in the said embodiment, although the holder | retainer 5 which has a ring part only in the axial direction one side of a pillar part is used, you may use the holder | retainer which has a ring part in the both ends of a pillar part. In the above embodiment, the tapered surface 14 is formed on the inner periphery of the cage 5 so as to gradually increase in diameter from the guided surface 13 toward the one side in the axial direction. A plurality of stepped steps that gradually increase in diameter toward one side in the axial direction may be formed.

  1: Angular contact ball bearing (rolling bearing), 2: outer ring, 3: inner ring, 4: rolling element, 5: cage, 6: first seal (seal), 7: second seal (seal), 11: ring Part 12: pillar part 13: guided surface 14: tapered surface 19: chamfered part 31: first inner shoulder part (first shoulder part) 32: second inner shoulder part (second shoulder part) 32a: outer peripheral surface (guide surface), 45: first labyrinth gap (labyrinth gap), 55: second labyrinth gap (labyrinth gap), S: annular space

Claims (7)

An inner ring, an outer ring, a plurality of rolling elements provided between the inner ring and the outer ring, an annular cage for holding the rolling element, and grease filled in an annular space between the inner ring and the outer ring In order to prevent outflow, a pair of seals provided at both axial ends of the annular space are provided, and the seals are fixed to the outer ring and are non-contact seals that form a labyrinth gap with the inner ring. A rolling bearing,
A rolling bearing in which at least a part of the outer peripheral surface of the inner ring is a guide surface that guides the rotation of the cage. In the inner ring, a first shoulder is formed on one side in the axial direction, and a second shoulder having an outer diameter smaller than the outer diameter of the first shoulder is formed on the other side in the axial direction.
The rolling bearing according to claim 1, wherein an outer peripheral surface of the second shoulder portion is the guide surface.   The said retainer has a guided surface that is slidably opposed to the guide surface, and a tapered surface that gradually increases in diameter from the guided surface toward the one side in the axial direction. Rolling bearing.   The rolling bearing according to claim 2 or 3, wherein a chamfered portion is formed at an inner peripheral end edge on the other axial side of the cage.   The labyrinth gap between the non-contact seal on the other side in the axial direction and the inner ring is formed so that the grease can easily enter than the labyrinth gap between the non-contact seal on the one side in the axial direction and the inner ring. The rolling bearing according to any one of claims 2 to 4.   The path length of the labyrinth gap between the non-contact seal on the other side in the axial direction and the inner ring is shorter than the path length of the labyrinth gap between the non-contact seal on the one side in the axial direction and the inner ring. The rolling bearing according to any one of 2 to 5.   The retainer includes an annular part disposed on the second shoulder side, and a plurality of pillars provided to extend from the annular part to the first shoulder side. The rolling bearing according to any one of -6.

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