JP2008286296A - Cage for angular ball bearing and angular ball bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a cage for an angular ball bearing and the angular ball bearing excellent in high speed operation, capable of dispensing with an auxiliary facility, capable of simplifying a structure, and capable of restraining a cage noise in operation, especially the cage noise in start of operation from the cooled state. <P>SOLUTION: The cage 9 is guided to an inner peripheral surface of an outer ring 6, and a recessed part 10L recessed to a radial inner part and reserving grease is provided in circumferential plural portions of a guide surface part 6c of the outer ring 6. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a cage for an angular ball bearing and a structure of an angular ball bearing in which measures for cage noise of an outer ring guide cage are taken.

A conventional angular ball bearing and its cage will be described with reference to FIG. Grease-lubricated angular ball bearings are put to practical use. For example, an outer ring guide type cage 1 is applied to this angular ball bearing. Some grease lubricated angular ball bearings are provided with a seal 2 for sealing the bearing space between the inner and outer rings in order to retain a large amount of grease. Furthermore, the present applicant has put into practical use an angular ball bearing, a so-called BNS series, in which a grease reservoir 3b is formed in the vicinity of the raceway surface 3a of the outer ring 3 to increase the amount of grease charged (for example, Non-Patent Document 1). The BNS series angular contact ball bearings have a longer life than standard angular contact ball bearings.
NTN Corporation precision rolling bearing CAT. No. 2260-II / J 04.09.03 (page 57, figure 9.8)

  For example, when the outer ring guide type cage 1 made of phenol resin is operated with grease lubrication, an annoying noise, that is, a cage noise may be generated in a low speed operation region. In particular, the cage noise is noticeably generated during warm-up operation at the beginning of the day, and the cage noise often subsides in the high speed operation region.

  As countermeasures for the cage noise, (1) the cage guide type is not the outer ring guide but the rolling element guide type, and (2) air oil lubrication is used. However, the rolling element guide type (1) is inferior in speed to the outer ring guide type. In (2) air-oil lubrication, there is a problem that ancillary facilities are required. Since this incidental equipment is required, the structure becomes complicated and the entire structure undesirably increases in size. Since the structure is complicated and the number of parts is increased, there is a problem that the manufacturing cost is increased.

  An object of the present invention is to improve the speed, simplify the structure by eliminating the need for ancillary equipment, etc., and suppress the cage noise during operation, particularly the cage noise at the start of operation from a cold state. A cage for ball bearings and an angular ball bearing are provided.

The angular ball bearing according to the present invention is an angular contact ball bearing having a cage guided to the inner peripheral surface of the outer ring, and supplies grease or a base oil of grease to the guide surface portion of the inner peripheral surface of the outer ring. A lubricant supply mechanism is provided.
According to this configuration, the lubricating oil supply mechanism is provided inside the bearing, and grease or base oil is supplied to the guide surface portion of the inner peripheral surface of the outer ring by the lubricating oil supply mechanism. Thus, since the lubricating oil from the lubricating oil supply mechanism contributes to the lubrication of the guide surface portion of the outer ring, the generation of cage noise can be suppressed. In addition, since there is no need to provide additional equipment outside the bearing, the structure can be simplified and the overall structure can be reduced in size. In addition, since it is an outer ring guide type, it is superior in speed to the rolling element guide type cage, and the structure can be simplified as compared with the air-oil lubricated type.

  In this invention, the cage is guided by a guide surface portion of an inner peripheral surface of an outer ring, and the lubricant supply mechanism is radially inward at a plurality of locations in the circumferential direction of the guide surface portion of the outer ring. It may include the one provided with a concave portion for storing grease.

  According to this configuration, concave portions are provided at a plurality of locations in the circumferential direction of the guide surface portion of the outer ring, and grease is stored in these concave portions. The accumulated grease contributes to the lubrication of the guide surface of the outer ring guide type retainer during the bearing operation, and the generation of the retainer noise can be suppressed. Therefore, generation | occurrence | production of a holder | retainer sound can be suppressed also at the time of the warming-up operation from the cold state, such as the time of the driving | operation start of the day.

  In the present invention, it is desirable that the ratio of the concave-shaped portion of the outer ring is specified to be 20% or more and 30% or less of the entire circumference. When the ratio of the concave portion of the outer ring is less than 20% of the entire circumference, a necessary and sufficient lubricant that can contribute to lubrication cannot be retained. If the ratio of the concave-shaped portion exceeds 30% of the entire circumference, the phase of one concave-shaped portion in the axial direction and the other concave-shaped portion in the axial direction are likely to be the same phase, and the behavior of the cage during operation is unstable. There is a risk of becoming. In other words, by defining the ratio of the concave-shaped portion of the outer ring to 20% or more and 30% or less of the entire circumference, it is possible to hold a necessary and sufficient lubricant that contributes to lubrication and to stabilize the behavior of the cage during operation. can do.

In the present invention, the concave portion has one concave shape portion in the axial direction of the outer ring and the other concave shape portion in the axial direction, and the phase of the one concave shape portion and the other concave shape portion is 45. You may arrange | position by shifting by 90 degree | times or 90 degree | times. In this case, the behavior of the cage during operation can be reliably stabilized.
In the present invention, grease storage grooves connected to the outer ring raceway grooves may be formed on both sides of the outer ring raceway grooves on the inner peripheral surface of the outer ring. In this case, the angular ball bearing can be speeded up.

  In the present invention, the lubricant supply mechanism is provided with a grease retaining groove for collecting grease in a radially outward direction on the inner diameter surface of the retainer, and communicates from the grease retaining groove to the outer diameter surface of the retainer. A through hole for allowing the base oil of the grease to pass therethrough is formed, and the base of the grease is formed on the outer peripheral surface of the retainer and the inner peripheral surface of the outer ring from the grease retaining groove through the through hole by rotation of the retainer. It is good also as what contains what enabled supply of oil.

  According to this configuration, the centrifugal force acts on the grease by rotation of the cage or the like, so that the base oil in the grease is separated and gradually the outer diameter surface of the cage and the inner ring of the outer ring from the through hole. It moves to the peripheral surface and contributes to lubrication. Thereby, generation | occurrence | production of a holder | retainer sound can be suppressed. Part of the base oil is supplied to the outer ring raceway surface, and the angular ball bearing can be speeded up.

  In this invention, the through-hole of the cage is provided at a plurality of locations in the circumferential direction, and the through-hole has one through-hole in the axial direction of the cage and the other through-hole in the axial direction. The holes and the other through-holes may be arranged out of phase. In this case, the behavior of the cage during operation can be reliably stabilized.

  An angular ball bearing retainer according to the present invention is an angular ball bearing retainer guided on an inner peripheral surface of an outer ring of an angular ball bearing, and is a grease that collects grease recessed outward in the radial direction on the inner diameter surface of the retainer. A reservoir groove is provided, and a through hole through which the grease base oil passes is formed by communicating with the outer diameter surface of the cage from the grease reservoir groove.

  According to this configuration, the grease stored in the grease storage groove of the cage is in a state where the thickener is mixed and dispersed in the base oil, that is, the base oil. In this state, a centrifugal force acts on the grease by the rotation of the cage or the like, so that the base oil of the grease is separated and gradually the outer diameter surface of the cage and the inner peripheral surface, that is, the inner peripheral surface, that is, It moves to the cage guide surface of the outer ring and contributes to lubrication. Thereby, generation | occurrence | production of a holder | retainer sound can be suppressed. The remaining grease and thickener in the grease reservoir groove contribute to lubrication of the raceway surfaces of the inner and outer rings of the angular ball bearing by the rotation of the cage. Therefore, an angular ball bearing retainer that is superior in speed than the rolling element guide type retainer, simplifies the structure, and can suppress the retainer noise during operation is achieved. be able to.

In the present invention, the through hole communicates with a portion guided by the outer ring on the outer diameter surface of the cage. In this case, the base oil of the grease is reliably supplied to the location guided by the outer ring on the outer diameter surface of the cage, and the generation of the cage noise can be suppressed.
In this invention, the grease retaining groove of the cage may be a circumferential groove along the circumferential direction. In this case, the grease retaining groove can be easily processed, and the grease can be retained over the entire circumference.
In the present invention, a plurality of through holes of the cage may be formed at regular intervals in the circumferential direction. In this case, more base oil can be supplied to the inner peripheral surface of the outer ring. Therefore, the cage noise during operation can be surely and quickly suppressed.

  The angular ball bearing according to the present invention is an angular contact ball bearing having a cage guided to the inner peripheral surface of the outer ring, and supplies grease or a base oil of grease to the guide surface portion of the inner peripheral surface of the outer ring. Since the lubricant supply mechanism is provided, it is excellent in high speed, simplifies the structure by eliminating the need for incidental equipment, etc., and suppresses the cage noise during operation, especially at the start of operation from a cold state. Can do.

  The angular ball bearing cage of the present invention is formed with a through hole that allows the grease base oil to pass through from the grease retaining groove on the inner diameter surface to the outer diameter surface of the cage. It is possible to simplify the structure by eliminating equipment and the like, and it is possible to suppress cage noise during operation, in particular, cage noise at the start of operation from a cold state.

  A first embodiment of the present invention will be described with reference to FIGS. The angular ball bearing according to this embodiment is applied to, for example, a machine tool spindle. However, it is not limited to the machine tool spindle. In this angular ball bearing, a ball 7 is interposed between an inner ring 5 and an outer ring 6, and the bearing space between the inner ring 5 and the outer ring 6 is sealed with seals 8 and 8 and used for grease lubrication. The The seal 8 is a non-contact type seal that is attached to the seal groove 6 a of the outer ring 6 and whose inner diameter side end is close to the inner ring 5. The balls 7 are held by a cage 9 so as to roll freely at a predetermined interval in the circumferential direction. A raceway groove 5a and a raceway groove 6b are provided on the outer peripheral surface of the inner ring 5 and the inner peripheral surface of the outer ring 6 so that the contact angle with the ball 7 is a predetermined angle.

  The cage 9 is formed in a ring shape so that the wall thickness Hn is constant over the entire circumference. A cylindrical hole-shaped pocket Pt that holds the ball 7 in a rollable manner is formed at the center in the width direction of the cage 9. A plurality of pockets Pt are arranged at regular intervals in the circumferential direction. The cage 9 is made of, for example, a resin material such as phenol resin or a metal cut-out product, and is guided to the guide surface portion 6 c on the inner peripheral surface of the outer ring 6. Moreover, the corner | angular part between the outer side wall part 9a of this holder | retainer 9 and the holder | retainer internal diameter 9b is given the corner chamfering 9c over the perimeter.

  On the inner peripheral surface of the outer ring 6, a grease storage groove 6 m is formed in the vicinity of both sides in the axial direction of the raceway groove 6 b. The grease storage groove 6 m forms an annular concave portion that is recessed radially outward from the outer ring guide surface portion 6 c. The grease storage groove 6m is connected to the raceway groove 6b on the inner peripheral surface of the outer ring 6, and is formed on the left and right sides of the raceway groove 6b shown in FIG. The grease storage groove 6m is provided in a range where a contact angle between the raceway groove 6b and the ball 7 is ensured.

  Outer ring guide surface portions 6c and 6c for guiding the cage outer diameter surface 9d are provided on the inner peripheral surface of the outer ring 6 on the axially inner side of the outer ring seal groove 6a and the axially outer side of the grease storage groove 6m. It has been. Concave portions 10 serving as a lubricant supply mechanism are provided at a plurality of locations in the circumferential direction of each outer ring guide surface portion 6c so as to store the grease Gr inward in the radial direction. That is, the concave portion 10L is provided in one axial direction of the outer ring 6, that is, the outer ring guide surface portion 6c on the left side of FIG. Part 10R is provided. The phases of the one concave shape portion 10L and the other concave shape portion 10R are shifted by a predetermined angle α1 in order to reliably stabilize the behavior of the cage 9 during operation.

  In the first embodiment, as shown in FIGS. 2 and 5, the predetermined angle α1 is set to 90 degrees, for example. However, the predetermined angle α1 is not limited to 90 degrees. Since the one and the other concave-shaped portions 10L and 10R have the same shape only by shifting the phase, the one concave-shaped portion 10L will be described in detail, and the other concave-shaped portion 10R will be described as one concave-shaped portion. The same reference numerals as those assigned to 10L are attached and detailed description thereof is omitted.

  As shown in FIG. 2 and FIG. 3, concave portions 10 </ b> L are formed at two locations in the circumferential direction on the outer ring guide surface portion 6 c that are symmetric with respect to 180 degrees. In order to hold the necessary and sufficient grease Gr (Fig. 3) that contributes to lubrication and to stabilize the behavior of the cage 9 during operation, the ratio of these concave-shaped portions 10L is 20% or more and 30% or less of the entire circumference. It is stipulated in. In the first embodiment, for example, the ratio of each concave shape portion 10L with respect to the entire circumference is defined as a predetermined angle β1, and a value obtained by multiplying the predetermined angle β1 by the number “2” of the concave shape portions 10L over the entire circumference. , It is specified to be 20% or more and 30% or less of the entire circumference. The predetermined angle β1 is set to 40 degrees, for example. However, the predetermined angle β1 is not limited to 40 degrees.

  The value obtained by multiplying the aforementioned predetermined angle β1 of 40 degrees by the number “2” of the concave portion 10L on one side is divided by the angle “360” of the entire circumference, and the value obtained by multiplying this value by “100” is About 22%. Therefore, this value falls within a specified numerical range, that is, 20% to 30% of the entire circumference. Thereby, it is possible to hold the necessary and sufficient grease Gr contributing to lubrication in the concave portions 10L and 10R and to stabilize the behavior of the cage 9 during operation. When the ratio of the concave portions 10L and 10R is less than 20% of the entire circumference, the necessary and sufficient grease Gr that can contribute to lubrication cannot be held. If the ratio of the concave-shaped portions 10L and 10R exceeds 30% of the entire circumference, the phases of the one and the other concave-shaped portions 10L and 10R in the axial direction are likely to be the same phase, and the behavior of the cage 9 is unstable during operation. There is a risk of becoming.

  Each concave-shaped portion 10L is formed so as to be recessed outward in the radial direction from the outer ring guide surface portion 6c and slightly inward in the radial direction from the grease storage groove 6m in the range of the predetermined angle β1 in the entire circumference. ing. Moreover, as shown in FIG. 3, the circumferential direction one end part 11a of each concave shape part 10L continues to the outer ring | wheel guide surface part 6c via the partial circular arc-shaped part 12, and the circumferential direction other end part 11b of each concave shape part 10L is also comprised. The outer ring guide surface portion 6 c is continued through the partial arc-shaped portion 12. The partial arc-shaped portion 12 has a radius of curvature R smaller than the radius of curvature of the concave-shaped portion 10L, and the boundary between the partial arc-shaped portion 12 and the concave-shaped portion 10L is formed without a step. The concave-shaped portion 10L and the partial arc-shaped portion 12 are, for example, concave-shaped portions that relatively move along the circumferential direction by pressing an unillustrated grinding wheel that is rotatable around the axial direction L1 against the outer ring guide surface portion 6c. The grinding wheel corresponding to 10L and the partial arcuate part 12 is formed by machining such as turning around an axis perpendicular to the axial direction L1. However, it is not limited only to these machining, and cutting or the like may be used.

On the outer peripheral surface of the inner ring 5, a counter bore 5 b is provided on one side of the raceway groove 5 a, the outer diameter of which gradually becomes smaller toward the end surface. The counter bore 5b is provided on a portion of the outer peripheral surface opposite to the direction in which the contact angle occurs.
At the time of assembling the bearing, grease Gr is stored in the concave-shaped portions 10L and 10R of the outer ring 6, and the outer ring 6 assembled with the balls 7 is heated, so that the outer ring 6 is heated to a predetermined small distance outward in the radial direction. It can be assembled by expanding and inserting the inner ring 5 in the axial direction from the counter bore 5b side. Grease used for lubricating the raceway surfaces 5a and 6b and the like is enclosed, for example, from the cage inner diameter 9b side of the cage 9 and the counter bore 5b side of the inner ring 5 before the seal 8 is assembled.

  According to the angular ball bearing described above, the concave-shaped portions 10L and 10R are provided at two locations in the circumferential direction of the outer ring guide surface portion 6c, and the grease Gr is stored in these concave-shaped portions 10L and 10R. The accumulated grease Gr contributes to the lubrication of the guide surface of the outer ring guide type cage 9 during the bearing operation, and the generation of cage noise can be suppressed. In particular, the occurrence of cage noise can be suppressed even during warm-up operation from a cold state, such as at the start of a day's operation. Further, since it is an outer ring guide type, it is superior in speed to the rolling element guide type cage and is grease lubricated, so that it is possible to simplify the structure by eliminating the need for incidental facilities and the like than those of air oil lubrication. As described above, it is possible to realize an angular ball bearing that is excellent in high-speed performance and can suppress the cage noise during operation while eliminating the need for incidental equipment.

  In addition, since the phase of the concave shape portion 10L on the one side in the axial direction and the concave shape portion 10R on the other side in the axial direction are shifted by a predetermined angle α, the behavior of the cage 9 during operation can be reliably stabilized. Is possible. In addition, the grease storage grooves 6m connected to the raceway grooves 6b are formed on both sides of the raceway grooves 6b on the inner peripheral surface of the outer ring 6 so that the contact angle between the raceway grooves 6b of the outer ring 6 and the balls 7 is secured. The grease Gr is unlikely to scatter from the grease storage groove 6m to the outside, so that a good lubrication state can be maintained, and the angular ball bearing can be speeded up.

  When forming the concave-shaped portions 10L and 10R and the partial arc-shaped portion 12 by pressing the grinding wheel capable of rotating around the axial direction L1 against the outer ring guide surface portion 6c and moving along the circumferential direction, By adjusting the amount of movement of the grindstone in the circumferential direction, etc., the recessed portions 10L and 10R having various predetermined angle β1 ranges can be obtained. That is, the dual use of the grinding wheel can be improved, and the concave shaped portions 10L and 10R having various predetermined angles β1 can be obtained with the grinding wheel. The grinding wheel may be moved in the circumferential direction with respect to the outer ring 6, or the outer ring 6 may be moved, that is, rotated in the circumferential direction with respect to the grinding wheel. When a dedicated grinding wheel corresponding to the concave-shaped portions 10L and 10R and the partial arc-shaped portion 12 is applied, the processing time can be shortened, and the man-hour can be reduced accordingly.

  Next, a second embodiment of the present invention will be described with reference to FIGS. This will be described with reference to FIG. In the following description, portions corresponding to the matters described in the first embodiment are denoted by the same reference numerals, and overlapping descriptions may be omitted. When only a part of the configuration is described, the other parts of the configuration are the same as those in the first embodiment. Not only the combination of the parts specifically described in each embodiment, but also the embodiments can be partially combined as long as the combination does not hinder.

  In the second embodiment, as shown in FIG. 6 and FIG. 8, concave portions 10L, 10R are formed at four locations in the circumferential direction on the outer ring guide surface portion 6c at intervals of 90 degrees in the circumferential direction. Yes. Further, one concave shape portion 10L in the axial direction is arranged with a predetermined angle α2 and shifted in phase with respect to the other concave shape portion 10R. The predetermined angle α2 is set to 45 degrees, for example, in order to reliably stabilize the behavior of the cage 9 during operation. Further, the predetermined angle β2 with respect to the entire circumference of each of the concave shaped portions 10L and 10R is set to 25 degrees, for example. However, the predetermined angle α2 is not limited to 45 degrees, and the predetermined angle β2 is not limited to 25 degrees.

  The value obtained by multiplying the predetermined angle β2 of 25 degrees by the number “4” of the concave portions 10L and 10R on one side is divided by “360” of the entire circumference, and the value obtained by multiplying this value by “100” is About 28%. Therefore, this value falls within a specified numerical range, that is, 20% to 30% of the entire circumference. As a result, necessary and sufficient grease that contributes to lubrication can be held in the recessed portions 10L and 10R, and the behavior of the cage 9 during operation can be stabilized. According to the angular ball bearing according to the second embodiment, the same operations and effects as the angular ball bearing according to the first embodiment are exhibited.

  Next, a third embodiment of the present invention will be described with reference to FIGS. In the following description, portions corresponding to the matters described in the first and second embodiments are denoted by the same reference numerals, and redundant descriptions may be omitted. When only a part of the configuration is described, the other parts of the configuration are the same as those in the preceding embodiment. Not only the combination of the parts specifically described in each embodiment, but also the embodiments can be partially combined as long as the combination does not hinder.

The grease retaining groove, the through hole and the like of the cage 9 according to the third embodiment will be described. The grease retaining groove and the through hole of the cage 9 correspond to a lubricant supply mechanism.
Grease retaining grooves 10A and 10A are formed on both side portions in the width direction of the inner diameter surface of the cage 9. These grease retaining grooves 10A and 10A are circumferential grooves along the circumferential direction, and are formed symmetrically as shown in FIG. Each grease retaining groove 10A has a groove bottom 10a, an outer wall portion 10b, and an inner wall portion 10c. The groove bottom 10a, the outer wall portion 10b, and the inner wall portion 10c have a substantially concave cross section. . The outer wall portion 10b erected from the outer portion in the width direction of the groove bottom 10a is a wall surface perpendicular to the cage axial direction L1, and the corner between the outer wall portion 10b and the cage inner diameter surface Hdb A chamfer 11 is applied over the circumference. Further, the thickness h1 between the outer wall 10b and the cage end surface Ht, that is, the axial thickness is, for example, about 1 of the thickness ha from the outer edge 12 of the pocket Pt of the cage 9 to the cage end surface Ht. / 2. The groove bottom 10a is formed in a cylindrical surface parallel to the cage axis L1. The radial thickness between the groove bottom 10a and the cage outer diameter surface 9d is slightly larger than ½ of the thickness Hn from the cage inner diameter surface Hdb to the cage outer diameter surface 9d. It is prescribed.

  The inner wall portion 10c is erected from the inner side in the width direction of the groove bottom 10a. The inner wall portion 10c is formed in a slope shape that is inclined toward the center in the width direction from the groove bottom 10a toward the cage inner diameter surface Hdb. The inclination angle α of the inner wall portion 10c is defined, for example, at 45 degrees with respect to the cage axis L1. However, the inclination angle α is not limited to 45 degrees.

  A through hole 13 that communicates from the groove bottom 10a to the outer diameter surface 9d of the cage is formed in the grease retaining groove 10A. The through hole 13 is formed to have a hole diameter that allows the base oil of the grease Gr to pass therethrough. As shown in FIG. 11, a plurality of through holes 13 of the cage 9 are formed at regular intervals in the circumferential direction. Further, in the cage 9, one end in the axial direction, that is, the plurality of through holes 13 at the right end in FIG. 11, and the other end in the axial direction, that is, the plurality of through holes 13 in the left end in FIG. Are formed at the same phase, that is, at the same left and right positions so as not to be in a staggered arrangement. Furthermore, as shown in FIG. 11, the left and right through holes 13 are disposed at positions in the retainer 9 that are in the same phase in the column portion 14 between the pockets adjacent in the circumferential direction.

  Each through-hole 13 is a so-called straight hole having an inclination angle β toward the outside in the width direction of the cage 9 as it goes from the cage inner diameter surface Hdb to the cage outer diameter surface 9d. For example, it is set to about 60 degrees with respect to the cage axis L1. However, the inclination angle β is not limited to 60 degrees. Of each through hole 13 of the cage 9, a portion that opens to the cage outer diameter surface 9 d is defined to be a position facing the outer ring guide surface 6 c. In particular, an opening portion of each through hole 13 is disposed in the vicinity of the intersection 6 cm of the outer ring guide surface 6 c with the outer ring grease retaining groove 6 m. By the rotation of the cage 9, the base oil of the grease Gr can be supplied from the grease retaining groove 10 </ b> A of the cage 9 to the cage outer diameter surface 9 d and the outer ring guide surface 6 c through the through hole 13.

As the grease Gr to be applied, for example, a sodium / barium-based grease Gr that is a metal soap-based grease is preferable as a grease that easily separates the base oil. Specifically, for example, a sodium / barium-based grease composed of a thickener: barium complex soap, base oil: ester oil, and base oil viscosity: 20 is applied.
As the grease Gr to be applied, for example, SE-1: thickener: urea, base oil: ester oil, base oil viscosity: 22 MP-1: thickener: urea, base oil: synthetic oil A grease with a base oil viscosity of 40.6, which is difficult to separate the base oil, may be applied depending on the usage conditions such as the rotational speed.

  According to the angular ball bearing described above, the grease Gr stored in the grease storage groove 10A of the retainer 9 is in a state where the thickener is mixed and dispersed in the base oil, that is, the base oil. In this state, a centrifugal force acts on the grease Gr by the rotation of the cage 9 and the like, whereby the base oil in the grease Gr is separated and gradually from the through hole 13 the cage outer diameter surface 9d and the outer ring guide surface. It moves to 6c and contributes to lubrication. Thereby, generation | occurrence | production of a holder | retainer sound can be suppressed. In particular, the occurrence of cage noise can be suppressed even during warm-up operation from a cold state, such as at the start of a day's operation. The remaining grease Gr and the thickener in the grease retaining groove 10A contribute to lubrication of the raceway surfaces 5a and 6b of the inner and outer rings 5 and 6 by the rotation of the cage 9. Therefore, to achieve an angular ball bearing cage that is superior to rolling element guide type cages, has a simpler structure than air-oil lubricated ones, and can suppress cage noise during operation. Can do. Further, a part of the base oil is supplied to the outer ring raceway surface 6b from the outer ring grease reservoir groove 6m, and the angular ball bearing can be speeded up.

  Since the grease retaining groove 10A of the retainer 9 is a circumferential groove along the circumferential direction, the grease retaining groove 10A can be easily machined by, for example, turning, and the entire circumferential direction can be processed. The grease Gr can be accumulated over the circumference. Further, since a plurality of through holes 13 of the cage 9 are formed at regular intervals in the circumferential direction, a larger amount of base oil can be supplied to the outer ring guide surface 6c. Therefore, the cage noise during operation can be surely and quickly suppressed.

  Since the grease retaining grooves 10A and 10A on both sides in the width direction are formed symmetrically as shown in FIG. 9, the center of gravity of the cage can be prevented from being biased and the speed can be increased. Further, the thickness h1 between the outer wall portion 10b and the cage end surface Ht is regulated to, for example, about 1/2 of the thickness ha from the outer edge 12 of the pocket Pt to the cage end surface Ht, and the groove bottom The thickness in the radial direction between 10a and the cage outer diameter surface 9d was defined to be slightly larger than ½ of the thickness Hn from the cage inner diameter surface Hdb to the cage outer diameter surface 9d. Accordingly, it is possible to maintain the predetermined rigidity and strength of the cage 9 and to reduce the weight of the cage 9.

Since the inner wall portion 10c of the grease retaining groove 10A of the retainer 9 is formed in a slope shape that inclines toward the center in the width direction from the groove bottom 10a toward the retainer inner diameter surface Hdb, it is retained in the grease retaining groove 10A. The grease Gr can be reliably fed into the groove bottom 10a along the slope by the centrifugal force.
Of each through hole 13 of the cage 9, a portion that opens to the cage outer diameter surface 9 d is defined to be a position facing the outer ring guide surface 6 c. In particular, since the opening portion of each through hole 13 is disposed in the vicinity of the intersection 6 cm with the outer ring grease retaining groove 6 m in the outer ring guide surface 6 c, the base oil is supplied from the through hole 13 by the rotation of the cage 9. The outer ring guide surface 6c and the outer ring grease retaining groove 6m can be suitably branched and supplied. The base oil supplied to the outer ring guide surface 6c suppresses the generation of cage noise, and the base oil supplied to the outer ring grease reservoir groove 6m serves to lubricate the raceway surfaces 5a and 6b of the inner and outer rings 5 and 6. Is done. In this way, it is possible to branch into a base oil that suppresses the generation of cage noise and a base oil that is used for lubrication of the raceway surfaces 5a and 6b without increasing the number of parts.
Since the left and right through-holes 13 are formed in the pillar portion 14 between the pockets Pt adjacent in the circumferential direction in the cage 9, it is possible to suppress a decrease in the rigidity strength of the cage 9 and during the bearing operation. It is possible to prevent the retainer 9 from being undesirably deformed due to the centrifugal force acting on the retainer 9.

  FIG. 12 is a partially broken bottom view of a modified form of the cage in which the phase of the through hole is shifted. In the cage shown in FIG. 11 described above, the plurality of through holes 13 at the right end and the plurality of through holes 13 at the left end are formed at the same phase in the circumferential direction. As shown in FIG. 12, the cage 9 according to this modified embodiment is arranged by shifting the phases in the circumferential direction of the plurality of through holes 13 at the left end and the plurality of through holes 13 at the right end. Yes. That is, the cage 9 is formed so that the left and right through holes 13 are arranged in a staggered manner. However, the left and right through-holes 13 are disposed not on the left and right sides of the pocket Pt but on the column portion 13 between the pockets Pt adjacent in the circumferential direction. Other configurations are the same as those shown in FIGS. In this case, the behavior of the cage 9 during operation can be reliably stabilized. Further, since the number of through holes 13 is reduced as compared with the cage shown in FIG. 11, the rigidity of the cage 9 can be increased accordingly. In addition, the same effects as those shown in FIGS. 10 and 11 are obtained.

  FIG. 13 is a cross-sectional view of a main part of an angular ball bearing according to the fourth embodiment of the present invention. This angular ball bearing is provided with concave portions 10 for storing grease Gr at a plurality of locations in the circumferential direction of the left and right outer ring guide surface portions 6c, and the cage bottom 10a of the grease reservoir groove 10A of the cage 9 A through hole 13 communicating with the outer diameter surface 9d is formed. The grease retaining groove 10A, the through hole 13, and the concave shape portion 10 of each outer ring guide surface portion 6c correspond to the lubricant supply mechanism.

The through holes 13 in this case may be formed at positions where the left and right through holes 13 are in the same phase in the circumferential direction as shown in FIG. Moreover, as shown in FIG. 12, you may form in the position where the through-holes 13 on either side become a phase which differs in the circumferential direction.
According to the angular ball bearing according to the fourth embodiment, since the concave portion 10 and the through-hole 13 are provided as the lubricant supply mechanism, the cage noise during operation can be more reliably and quickly suppressed. it can. Further, for example, the grease Gr accumulated mainly in the concave portion 10 suppresses the cage noise during the low speed operation from the start of the operation, and mainly from the low speed operation to the high speed operation due to the base oil supplied from the through hole 13. It becomes possible to suppress the cage noise. Thus, the main body which suppresses a holder | retainer sound according to a driving speed can be shared. Therefore, the versatility to which this angular ball bearing can be applied can be enhanced. In addition, the same effects as those of the first to third embodiments are obtained.
In this embodiment, the cage is applied to an angular contact ball bearing with a seal, but may be applied to an open type angular contact ball bearing without a seal. Even in this case, the same operations and effects as the present embodiment are obtained.

It is sectional drawing of the angular contact ball bearing which concerns on 1st Embodiment of this invention. It is a side view showing the concave-shaped part of the outer ring left side surface of the angular ball bearing. It is an enlarged side view of the principal part (C section) of FIG. It is the IV-IV sectional view taken on the line of FIG. It is a side view showing the concave-shaped part of the outer ring right side surface of the angular ball bearing. It is a side view showing the concave-shaped part of the outer ring left side surface of the angular ball bearing which concerns on 2nd Embodiment of this invention. It is the VII-VII sectional view taken on the line of FIG. It is a side view showing the concave-shaped part of the outer ring right side surface of the angular ball bearing. It is sectional drawing of the angular ball bearing which concerns on 3rd Embodiment of this invention. It is an expanded sectional view of the principal part of the angular ball bearing. It is the bottom view which fractured | ruptured partially the retainer of the angular ball bearing. It is the partially broken bottom view of the change form of the same holder which shifted the phase of the penetration hole. It is sectional drawing of the principal part of the angular ball bearing which concerns on 4th Embodiment of this invention. It is sectional drawing of the angular ball bearing of a prior art example.

Explanation of symbols

5 ... Inner ring 6 ... Outer ring 6c ... Outer ring guide surface 6m ... Grease storage groove 7 ... Ball 9 ... Retainer 9d ... Retainer outer diameter surface 10A ... Grease reservoir groove 10L, 10R ... Concave-shaped portion 13 ... Through hole Gr ... Grease α1 , Α2 ... predetermined angle β1, β2 ... predetermined angle

Claims (11)

In the angular ball bearing having a cage guided to the inner peripheral surface of the outer ring,
An angular contact ball bearing characterized in that a lubricant supply mechanism for supplying grease or grease base oil to the guide surface portion of the inner peripheral surface of the outer ring is provided inside the bearing.   2. The cage according to claim 1, wherein the retainer is guided by a guide surface portion of an inner peripheral surface of the outer ring, and the lubricant supply mechanism is radially inward at a plurality of locations in the circumferential direction of the guide surface portion of the outer ring. Angular contact ball bearings, including those that are recessed and have a concave shape to store grease.   The angular ball bearing according to claim 2, wherein the ratio of the concave portion of the outer ring is specified to be 20% or more and 30% or less of the entire circumference.   4. The concave portion according to claim 2, wherein the concave portion has one concave shape portion in the axial direction of the outer ring and the other concave shape portion in the axial direction, and the one concave shape portion and the other concave shape portion. Angular contact ball bearings in which the phase is shifted by 45 degrees or 90 degrees.   5. The angular contact ball bearing according to claim 1, wherein grease storage grooves connected to the outer ring raceway groove are formed on both sides of the outer ring raceway groove on the inner peripheral surface of the outer ring.   6. The lubricant supply mechanism according to claim 1, wherein the lubricant supply mechanism is provided with a grease reservoir groove that is recessed radially outward in the inner diameter surface of the cage and retains the grease from the grease reservoir groove. A through hole is formed in communication with the outer diameter surface of the cage to allow the base oil of the grease to pass through. The outer diameter surface and outer ring of the cage are rotated from the grease retaining groove through the through hole by rotation of the cage. An angular ball bearing including a grease base oil that can be supplied to the inner peripheral surface of the bearing.   In Claim 6, The through-hole of the said holder | retainer is provided in the circumferential direction several places, It has one through-hole of the axial direction of the said holder | retainer, and another through-hole of the axial direction as these through-holes, Angular contact ball bearings in which the through hole and the other through hole are out of phase. In the angular ball bearing cage guided by the inner peripheral surface of the outer ring of the angular ball bearing,
A grease reservoir groove is provided on the inner diameter surface of the cage to store grease that is recessed radially outward. The grease reservoir groove communicates with the outer diameter surface of the cage, and has a through hole through which the base oil of the grease passes. A cage for an angular ball bearing characterized by being formed.   9. The angular ball bearing retainer according to claim 8, wherein the through hole communicates with a portion guided by the outer ring on an outer diameter surface of the retainer.   The angular ball bearing retainer according to claim 8 or 9, wherein the grease retaining groove of the retainer is a circumferential groove along a circumferential direction.   The angular ball bearing cage according to any one of claims 8 to 10, wherein a plurality of through holes of the cage are formed at regular intervals in the circumferential direction.

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