JP5739293B2 - Rolling bearing device - Google Patents

Description

  The present invention relates to a rolling bearing device that rotatably supports a machine tool main shaft, for example, and relates to a rolling bearing provided with a supply / discharge oil mechanism that supplies lubricating oil also serving as a bearing cooling medium into the bearing and discharges it outside the bearing. Relates to the device.

  There has been proposed a lubricating device having a mechanism for cooling a bearing and supplying and discharging lubricating oil to and from the bearing (Patent Document 1). In this lubricating device, as shown in FIG. 11, an inner ring spacer 50 in contact with the inner ring end face is provided, and a lubricating oil introducing member 51 in contact with the outer ring end face is provided. A circumferential groove 53 is provided on the slope of the inner ring 52 connected from the inner ring end surface to the inner ring raceway surface, a nozzle 54 is provided in the lubricating oil introduction member 51, and a bearing cooling medium is provided from the nozzle 54 into the circumferential groove 53. It is designed to discharge lubricating oil.

JP 2008-240946 A

  In the structure of FIG. 11, when a large amount of lubricating oil enters the bearing and the lubricating oil stays in the bearing, the stirring resistance increases, the temperature of the bearing rises, and high-speed rotation may be impossible. Therefore, it is necessary to smoothly drain the lubricating oil that has entered the bearing.

Here, the present applicant has proposed a rolling bearing device shown in FIG. As shown in the figure, the inner ring 1 is provided with an inner ring extension portion 6 that extends in the axial direction, and a spacer 7 that is adjacent to the outer ring 2 and whose inner peripheral surface faces the inner ring extension portion 6. In this case, during the operation of the bearing, the lubricating oil enters the bearing as shown in (1) to (5) below. The arrows in the figure indicate the flow of the lubricating oil.
(1) Supply lubricating oil from the oil supply passage 9.
(2) The lubricating oil hits the inner ring circumferential groove 8.
(3) The lubricating oil receives centrifugal force from the rotating inner ring 1 and hits the inner peripheral surface 7 a of the spacer 7.
(4) Lubricating oil enters the bearing from the radial clearance between the outer peripheral surface of the inner ring extension 6 and the inner peripheral surface of the spacer 7. At this time, when the rolling bearing device is used for supporting the vertical shaft, for example, the lubricating oil hitting the inner peripheral surface 7a is discharged too much at the oil discharge port due to the action of gravity or the like in the course of going to the oil discharge port. In some cases, a large amount may enter the bearing.
(5) When a large amount of lubricating oil enters in this way, the lubricating oil stays in the bearing. This accumulated lubricating oil causes heat generation of the bearing, and high speed operation becomes impossible.

  An object of the present invention is to provide a rolling bearing device capable of smoothly draining lubricating oil that has entered the bearing to the outside of the bearing and suppressing an increase in the temperature of the bearing due to the stirring resistance of the lubricating oil.

  The rolling bearing device according to the present invention supplies a rolling bearing in which a plurality of rolling elements held by a cage are interposed between the raceway surfaces of the inner and outer rings, and lubricating oil also serving as a bearing cooling medium into the bearing. In a rolling bearing device having an oil supply / discharge oil mechanism for discharging to the outside, an inner ring extension extending in the axial direction is provided on the inner ring, and a spacer adjacent to the outer ring and having an inner peripheral surface facing the inner ring extension is provided. The oil supply / discharge oil mechanism is provided with an inner ring circumferential groove provided on an outer peripheral surface of an inner ring extension, and an oil supply opening provided in the spacer and discharging lubricating oil toward the inner ring circumferential groove. A radial direction is provided between the outer peripheral surface of the outer ring of the inner ring extension and the inner ring circumferential groove formed on the bearing side and the inner peripheral surface of the spacer, and guides the lubricating oil into the bearing. A clearance and an inner ring provided in the spacer at a circumferential position different from the oil filler opening An oil discharge port that communicates with the circumferential groove and discharges lubricating oil, and is supplied from the oil supply port to the inner circumferential surface of the spacer so as to face the inner ring circumferential groove and bounces off at the inner ring circumferential groove. It is characterized in that a recess for collecting the lubricating oil is provided.

According to this configuration, when the lubricating oil is supplied from the oil supply passage of the spacer during the bearing operation, the lubricating oil flows along the inner ring circumferential groove on the outer peripheral surface of the inner ring extension. This cools the bearing. The oil that has cooled the bearing is discharged from the oil outlet of the spacer. At this time, the lubricating oil supplied from the oil supply passage and bounced off by the inner ring circumferential groove is collected in the recess of the inner peripheral surface of the spacer, thereby suppressing the intrusion of the lubricating oil into the bearing. The lubricating oil collected in the recess is smoothly discharged toward the oil discharge port. Also, an appropriate amount of lubricating oil for lubricating the bearing is supplied into the bearing through the radial clearance, and then discharged out of the bearing.
As described above, the lubricating oil bounced off by the inner ring circumferential groove can be collected in the recess provided on the inner peripheral surface of the spacer and smoothly discharged, so that a large amount of lubricating oil can be prevented from entering the bearing. it can. Therefore, it is possible to suppress the temperature rise of the bearing due to the stirring resistance of the lubricating oil and to enable high-speed rotation of the bearing.

The said recessed part may consist of a circumferential groove provided in the inner peripheral surface of the spacer. In this case, the lubricating oil flows along the circumferential groove, and this lubricating oil can be smoothly discharged from the oil discharge port.
Among the recesses, the axial position of the opening peripheral part connected to the radial clearance and the axial position of the opening peripheral part connected to the radial clearance of the inner ring circumferential groove are matched, and the recess and the inner ring The width dimension of the circumferential groove may be the same. Lubricating oil in the inner ring circumferential groove receives centrifugal force from the rotating inner ring and proceeds in the direction of the spacer. At this time, the lubricating oil passes through the upper portion of the radial clearance by matching the axial positions of the opening peripheral edge of the recess and the opening peripheral edge of the inner ring circumferential groove. For this reason, it becomes difficult for the lubricating oil to enter the bearing, and the lubricating oil that has passed through the upper portion of the radial clearance goes to the oil outlet. Furthermore, by making the width of the recess and the inner ring circumferential groove the same, the lubricating oil present in the inner ring circumferential groove is reliably collected in the recess by centrifugal force from the inner ring, and the lubricant is not desired from the recess. Can be prevented from overflowing. Therefore, it is possible to prevent the lubricating oil from being undesirably discharged from locations other than the oil discharge port.

  The said recessed part is good also as what becomes narrow as it goes to the bottom face. During the bearing operation, the lubricating oil hits the inner ring circumferential groove and is rebounded by the centrifugal force accompanying the inner ring rotation. The rebounded lubricating oil travels toward the oil discharge port along a groove having a narrow recessed portion, in other words, a wedge-shaped groove. Thereafter, the lubricating oil is discharged from the oil discharge port. Since the lubricating oil is directed to the oil discharge port along the groove that becomes narrower in the recessed portion, the lubricating oil bounced back against the inner ring circumferential groove can be efficiently collected in the recessed portion.

Even if the said recessed part has the circumferential groove provided in the inner peripheral surface of the spacer and the circumferential groove which is connected to the lower part of this circumferential groove and whose width dimension is larger than the said circumferential groove. good. In this case, the lubricating oil bounced off against the inner ring circumferential groove can be collected in the circumferential groove having the large width dimension and smoothly drained.
It is good also as what provided the drainage port of the said spacer in the tangent direction connected to the circumferential groove of this spacer. In this case, the lubricating oil supplied from the spacer oil supply port bounces off the inner ring circumferential groove, flows along the circumferential groove of the spacer, and is smoothly discharged without staying at the oil discharge port.

You may provide the said recessed part in the circular arc shape from the oil filler opening of a spacer to an oil drain outlet. In this case, the lubricating oil flowing through the recess of the spacer is blocked by the oil discharge port. The blocked lubricating oil is quickly discharged from the oil discharge port.
The inner ring circumferential groove may have oil repellency. In this case, the lubricating oil existing in the inner ring circumferential groove can be easily directed to the recessed portion of the spacer, and smooth draining can be performed.

A slope formed in a cross-sectional shape that is inclined so as to become larger in diameter toward the raceway surface side between the inner raceway surface and the portion forming the radial clearance in the outer peripheral surface of the inner ring. It may be. In this case, the lubricating oil introduced into the bearing from the radial clearance can be reliably and appropriately guided to the inner ring raceway surface via the slope of the inner ring by the centrifugal force generated by the inner ring rotation.
The rolling bearing may be an angular ball bearing.
Any of the rolling bearing devices of the present invention may be used for supporting a machine tool spindle.

  The rolling bearing according to the present invention supplies a rolling bearing in which a plurality of rolling elements held by a cage are interposed between the raceway surfaces of the inner and outer rings, and a lubricating oil that also serves as a bearing cooling medium into the bearing. In the rolling bearing device having an oil supply / discharge oil mechanism for discharging to the inner ring, an inner ring extension extending in the axial direction is provided on the inner ring, and a spacer adjacent to the outer ring and having an inner peripheral surface facing the inner ring extension is provided. ing. The oil supply / discharge oil mechanism includes an inner ring circumferential groove provided on an outer peripheral surface of an inner ring extension, and an oil supply path provided in the spacer and having an oil supply port that discharges lubricant toward the inner ring circumferential groove. A radial clearance provided between the outer peripheral surface of the inner ring extension portion on the bearing side of the inner ring circumferential groove and the inner peripheral surface of the spacer, and guiding the lubricating oil into the bearing; And provided in the spacer, communicated with the inner ring circumferential groove at a circumferential position different from the oil supply port, and has an oil discharge port for discharging lubricating oil, and on the inner peripheral surface of the spacer, Opposite to the inner ring circumferential groove, a recess is provided for collecting the lubricating oil supplied from the oil supply port and bounced back by the inner ring circumferential groove. For this reason, the lubricating oil that has entered the bearing can be smoothly drained out of the bearing, and the temperature rise of the bearing due to the stirring resistance of the lubricating oil can be suppressed.

It is sectional drawing of the rolling bearing apparatus which concerns on 1st Embodiment of this invention. It is sectional drawing of the principal part which shows the example of the shape of the spacer of the same rolling bearing apparatus. It is an enlarged view of the A section of FIG. (A) is a top view which shows the flow of the lubricating oil in the rolling bearing apparatus, (B) is a front view of the principal part of FIG. 4 (A). It is sectional drawing of the principal part of the rolling bearing apparatus which concerns on other embodiment of this invention. It is sectional drawing of the principal part of the rolling bearing apparatus which concerns on further another embodiment of this invention. It is a top view which shows the flow of the lubricating oil in the rolling bearing apparatus which concerns on further another embodiment of this invention. It is a top view which shows the flow of the lubricating oil in the rolling bearing apparatus which concerns on further another embodiment of this invention. It is sectional drawing of the rolling bearing apparatus which concerns on other embodiment of this invention. It is a schematic sectional drawing which shows the example which applied the rolling bearing apparatus which concerns on either embodiment of this invention to the rolling bearing which supports a machine tool main shaft. It is sectional drawing of the principal part of the lubricating device of the rolling bearing of a prior art example. It is sectional drawing of the principal part which shows the reference proposal example in which lubricating oil permeates into the inside of a bearing.

A first embodiment of the present invention will be described with reference to FIGS. As shown in FIG. 1, the rolling bearing device according to this embodiment includes a rolling bearing Br and a supply / discharge oil mechanism Ku.
As shown in FIG. 2, the rolling bearing Br includes a pair of bearing rings that are inner and outer rings 1 and 2, a plurality of rolling elements 3 interposed between the raceway surfaces 1 a and 2 a of the inner and outer rings 1 and 2, and these rolling elements. And a ring-shaped cage 4 that holds 3. The rolling bearing is an angular ball bearing, and a ball made of a steel ball, a ceramic ball or the like is applied as the rolling element 3.

The inner ring 1 has an inner ring main body 5 and an inner ring extension 6 extending integrally from the inner ring main body 5. In this example, the inner ring extension 6 extends in the width direction from the biased side of the action line L that forms a contact angle with the raceway surface 1 a of the inner ring main body 5. The inner ring main body 5 satisfies the necessary strength as a bearing, and has the same width as the outer ring 2 and is provided with a predetermined width. The predetermined width dimension is a width dimension of the inner ring defined in JIS, a bearing catalog or the like. A raceway surface 1 a is formed at the center of the outer peripheral surface of the inner ring main body 5. A slope formed in a cross-sectional shape that inclines so as to increase in diameter toward the raceway surface side on one side in the axial direction (between the raceway surface 1a and the radial clearance δ1) connected to the raceway surface 1a in the outer peripheral surface. 1b is formed, and a flat outer diameter surface 1c is formed on the other side in the axial direction connected to the track surface 1a of the outer peripheral surface. An inner ring extension 6 is integrally provided on the inner ring back side (bearing front side) of the inner ring main body 5 so as to extend in one axial direction.
An outer ring inner diameter surface 2b and a counter bore 2c are formed on both axial sides of the raceway surface 2a of the outer ring 2, respectively. The cage 4 is configured to be guided to the outer ring inner surface 2b.

  As shown in FIG. 1, the supply / discharge oil mechanism Ku is a mechanism that supplies lubricating oil that also serves as a bearing cooling medium into the bearing and discharges it outside the bearing. A spacer 7 is provided adjacent to the outer ring 2, and the inner peripheral surface of the spacer 7 is opposed to the outer peripheral surface of the inner ring extension 6. The oil supply / discharge oil mechanism Ku includes an inner ring circumferential groove 8, an oil supply passage 9, a radial clearance δ1, an oil discharge port 10, a recessed portion 11, and a slope 1b. Among these, the inner ring circumferential groove 8 is provided on the outer circumferential surface of the inner ring extension 6.

  As shown on the left side of FIG. 1, an oil supply passage 9 having an oil supply port 18 that discharges lubricating oil toward the inner ring circumferential groove 8 is formed in a part of the spacer 7 in the circumferential direction. The oil supply passage 9 is formed in a stepped through hole shape that penetrates the recess 11 in the radial direction from the outer peripheral surface of the spacer 7. In other words, the oil supply passage 9 is composed of a communication hole 9a that communicates with a part of the recess 8 formed of a circumferential groove in the circumferential direction, and a counterbore 9b that is connected to the communication hole 9a and opens to the outer peripheral surface. The counterbore 9b is concentric with the communication hole 9a and has a larger diameter than the communication hole 9a. As shown in FIG. 3, the lubricating oil supplied from the oil supply passage 9 is discharged from the oil supply port 18, hits the inner ring circumferential groove 8, receives a centrifugal force from the inner ring 1 that is the rotating raceway ring, and receives the spacer 7 Proceed to the dent 11. As shown in FIG. 4 (A), this lubricating oil proceeds in the same direction as the rotational direction L1 of the inner ring 1 through the recess 11 formed of a circumferential groove, and is discharged from the oil discharge port 10 and a notch 13 described later. Is done.

In the spacer 7, an oil discharge port 10 for discharging the lubricating oil to the outside is formed at a circumferential position different from the oil supply passage 9. As shown on the right side of FIG. 1, the oil discharge port 10 is formed so as to penetrate from the outer peripheral surface of the spacer 7 in the radial direction and communicate with the inner ring circumferential groove 8. As shown in FIG. 4 (A), the oil supply passage 9 is provided such that the phase of the oil discharge port 10 is a predetermined phase angle α (α = 270 degrees in this example).
As shown in FIG. 2, the radial clearance δ <b> 1 is between the outer peripheral surface of the inner ring extension 6 on the bearing side of the inner ring circumferential groove 8 and the inner peripheral surface of the spacer 7. Provided. The lubricating oil introduced into the bearing from the radial clearance δ1 is guided to the inner ring raceway surface 1a via the slope 1b and the like.

  The recess 11 is formed by a circumferential groove provided on the inner peripheral surface of the spacer 7. The recessed portion 11 is opposed to the inner ring circumferential groove 8 and collects lubricating oil supplied from the oil supply passage 9 and bounced back in the inner ring circumferential groove 8. Of the recess 11, the axial position P1 of the opening peripheral edge 12 connected to the aforementioned radial clearance δ1 and the axial position P2 of the opening peripheral edge 14 connected to the radial clearance δ1 of the inner ring circumferential groove 8 are defined. Match. Further, the width dimension H1 of the recess 11 and the width dimension H2 of the inner ring circumferential groove 8 are the same.

  The outer ring 2, which is a fixed-side raceway ring, is provided with a notch 13 that discharges lubricating oil used for lubrication in the bearing to the outside of the bearing. 4B is a front view (end view taken along line AA) of the main part of FIG. As shown in FIGS. 1 and 4B, a notch portion 13 is provided on the outer ring end surface of the outer ring 2 on the opposite side in the axial direction from the side where the spacer 7 is provided. As shown in FIG. 4A, the notch 13 is disposed between the oil supply passage 9 and the oil discharge port 10 along the rotation direction L <b> 1 of the inner ring 1. In this example, the notch 13 is disposed with a phase angle of 90 degrees with respect to the oil supply passage 9 and with a phase angle of 180 degrees with respect to the oil discharge port 10, for example.

  As shown in FIG. 2, the inner ring extension 6 and the spacer 7 are provided with, for example, a labyrinth mechanism 15 that suppresses leakage of lubricating oil into adjacent bearings. The labyrinth mechanism 15 communicates with the oil supply passage 9 and the oil discharge port 10 (FIG. 1), and the wide portion and the narrow portion are continuous in the axial direction. The wide portion includes a circumferential groove 16 provided on the outer circumferential surface of the other shoulder portion of the inner ring extension portion 6 and an inner circumferential surface of the spacer 7 facing the circumferential groove 16. A plurality (two in this example) of the circumferential grooves 16 are arranged at intervals in the axial direction. Each circumferential groove 16 has a cross-sectional shape that becomes smaller in diameter toward the end face side (upper side in FIG. 2) of the inner ring extension 6, in other words, is inclined so that the groove becomes deeper. The narrow portion includes a protruding tip 17 of the outer peripheral surface of the inner ring extension 6 and an inner peripheral surface of the spacer 7 facing the protruding tip 17.

  Since each circumferential groove 16 is formed in an inclined cross-sectional shape as described above, the lubricating oil supplied from the oil supply passage 9 and entering the labyrinth mechanism 15 is inclined by the centrifugal force due to the inner ring rotation. Move along the surface in the opposite direction to the leak side. Such a labyrinth mechanism 15 can prevent the lubricating oil from leaking into the adjacent bearing. Note that the number of circumferential grooves 16 may be three or more, or one. Instead of the configuration in which the circumferential groove 16 is provided in the inner ring extension 6, a circumferential groove may be provided in the other shoulder portion having a concave cross section in the spacer 7. Moreover, you may provide a circumferential groove in the inner ring extension part 6 and the spacer 7, respectively.

The effect will be described.
1 indicate the flow of the lubricating oil. As shown in FIG. 1, when the lubricating oil is supplied from the oil supply passage 9 of the spacer 7 during the bearing operation, the lubricating oil flows along the inner ring circumferential groove 8 on the outer peripheral surface of the inner ring extension 6. This cools the bearing. The oil that has cooled the bearing is discharged from the oil discharge port 10 of the spacer 7. At this time, the lubricating oil supplied from the oil supply passage 9 and bounced off by the inner ring circumferential groove 8 is collected in the recess 11 on the inner peripheral surface of the spacer 7 to suppress the intrusion of the lubricating oil into the bearing. Lubricating oil collected in the recess 11 formed of a circumferential groove flows along the circumferential groove and is smoothly discharged toward the oil discharge port 10. In addition, an appropriate amount of lubricating oil for lubricating the bearing is supplied into the bearing through the radial clearance δ1, and then discharged out of the bearing.
Since the lubricating oil bounced off by the inner ring circumferential groove 8 can be collected in the recess 11 provided on the inner peripheral surface of the spacer 7 as described above and discharged smoothly, a large amount of lubricating oil can enter the bearing. Can be prevented. Therefore, it is possible to suppress the temperature rise of the bearing due to the stirring resistance of the lubricating oil and to enable high-speed rotation of the bearing.

Further, during the bearing operation, as shown in FIG. 3, the lubricating oil present in the inner ring circumferential groove 8 receives a centrifugal force from the rotating inner ring 1 and advances toward the spacer 7. At this time, by matching the axial positions P1 and P2 between the opening peripheral edge 12 of the recess 11 and the opening peripheral edge 14 of the inner ring circumferential groove 8, the lubricating oil passes through the upper part of the radial clearance. For this reason, it becomes difficult for the lubricating oil to enter the bearing, and the lubricating oil that has passed through the upper portion of the radial clearance goes to the oil discharge port 10 (FIG. 1). Furthermore, by making the width dimensions H1, H2 of the recess 11 and the inner ring circumferential groove 8 the same, the lubricating oil present in the inner ring circumferential groove 8 is reliably collected in the recess 11 by the centrifugal force from the inner ring 1, It is possible to prevent the lubricant from overflowing from the recess 11 undesirably. Therefore, it is possible to prevent the lubricating oil from being undesirably discharged from locations other than the oil discharge port.
Between the raceway surface 1a and the portion forming the radial clearance δ1 on the outer peripheral surface of the inner ring main body 5, there is a slope 1b formed in a cross-sectional shape that is inclined so as to increase in diameter toward the raceway surface 1a. Therefore, the lubricating oil introduced into the bearing from the radial clearance δ1 can be guided to the raceway surface 1a in an appropriate amount through the inclined surface 1b by the centrifugal force generated by the inner ring rotation.

Another embodiment will be described.
In the following description, the same reference numerals are given to the portions corresponding to the matters described in the preceding forms in each embodiment, and the overlapping description is omitted. When only a part of the configuration is described, the other parts of the configuration are the same as those described in advance unless otherwise specified.

As shown in FIG. 5, the recessed part 11 of the spacer 7 is good also as what becomes narrow as it goes to the bottom face. In this case, the lubricating oil flows as shown in the following (1) to (3) during the bearing operation.
(1) The lubricating oil hits the inner ring circumferential groove 8 and is bounced back under the centrifugal force accompanying the inner ring rotation.
(2) The rebounded lubricating oil travels toward the oil discharge port 10 along a narrow groove of the recess 11, in other words, a wedge-shaped groove.
(3) Thereafter, the lubricating oil is discharged from the oil discharge port 10.
Thus, since the lubricating oil is directed to the oil discharge port 10 along the narrow groove of the dent 11, the lubricating oil bounced off against the inner ring circumferential groove 8 can be efficiently collected in the dent 11. .

  As shown in FIG. 6, the recessed part 11 of the spacer 7 is connected to the circumferential groove 11a provided on the inner peripheral surface of the spacer 7 and the lower part of the circumferential groove 11a, and is wider than the circumferential groove 11a. You may have the circumferential groove | channel 11b from which H1a becomes large. In this case, the lubricating oil bounced off by hitting the inner ring circumferential groove 8 can be collected in the circumferential groove 11b having a large width dimension and drained smoothly.

FIG. 7 is a plan view showing a flow of lubricating oil in a rolling bearing device according to still another embodiment. As shown in the figure, it may be provided in the tangential direction L2 connected to the oil drain port 10 of the spacer 7. In this case, the lubricating oil supplied from the oil supply passage 9 of the spacer 7 bounces back against the inner ring circumferential groove (not shown), flows along the circumferential groove 11 of the spacer 7, and stays at the oil discharge port 10. It is discharged smoothly without doing.
As shown in FIG. 8, the recess 11 of the spacer 7 may be provided in an arc shape extending from the oil supply passage 9 of the spacer 7 to the oil discharge port 10. In this case, the lubricating oil flowing through the recess 11 of the spacer 7 is blocked by the oil discharge port 10. The blocked lubricating oil is quickly discharged from the oil discharge port 10.

  As shown in part A of FIG. 9, the inner ring circumferential groove 8 may have oil repellency. By providing the inner ring circumferential groove 8 with, for example, a coating layer made of fluororesin or the like, the inner ring circumferential groove 8 having oil repellency can be obtained. In this case, the lubricating oil existing in the inner ring circumferential groove 8 can be easily directed to the recessed portion 11 of the spacer 7 so that smooth drainage can be performed. Further, as shown in part B of FIG. 9, the outer peripheral surface portion of the inner ring extension 6 and the inner peripheral surface portion of the spacer 7 which are portions that form the radial clearance δ1 may also have oil repellency. In this case, intrusion of the lubricating oil into the bearing can be suppressed.

  FIG. 10 is a cross-sectional view schematically showing an example in which any of the above-described rolling bearing devices is used to support a vertical machine tool spindle. In this example, two rolling bearing devices 28 and 28 including angular ball bearings are installed in the housing 29 in a combination of the back surfaces, and the main shaft 30 is rotatably supported by these rolling bearing devices 28 and 28. The inner ring 1 in each bearing device 28 is positioned in the axial direction by inner ring positioning spacers 31, 31 and step portions 30 a, 30 a of the main shaft 30, and is fastened and fixed to the main shaft 30 by an inner ring fixing nut 32. The spacer 7 on the upper side of the main shaft and the outer ring 2 on the lower side of the main shaft are positioned and fixed in the housing 29 by outer ring pressing lids 34 and 34. An outer ring spacer 35 is interposed between the outer ring end surface on the upper side of the main shaft and the spacer width surface on the lower side of the main shaft.

  The housing 29 is formed by fitting a housing inner cylinder 29a and a housing outer cylinder 29b, and an oil passage groove 29c for cooling is provided in the fitting portion. Supply oil passages 36 and 36 for supplying lubricating oil to the bearing devices 28 are formed in the housing inner cylinder 29a. These supply oil passages 36 are connected to a lubricating oil supply source (not shown). Further, the housing inner cylinder 29 a is formed with an oil drain groove 37 and an oil drain passage 38 for discharging the lubricating oil used for lubrication. The oil drain groove 37 communicates with the notch 13 and the oil drain port 10 in each bearing device 28. Each oil drain groove 37 is connected to an oil drain passage 38 extending in the main shaft axis direction, and the lubricating oil is discharged from the oil drain passage 38.

When the rolling bearing devices 28 and 28 are used for supporting the machine tool main shaft 30 as described above, the lubricating oil bounced off by the inner ring circumferential groove 8 is collected in the recess 11 provided on the inner circumferential surface of the spacer 7 to smoothly Therefore, a large amount of lubricating oil can be prevented from entering the bearing. Therefore, it is possible to suppress the temperature rise of the bearing due to the stirring resistance of the lubricating oil and to enable high-speed rotation of the bearing.
It is also possible to use the rolling bearing device according to the present embodiment for supporting a horizontal machine tool spindle.

DESCRIPTION OF SYMBOLS 1 ... Inner ring 2 ... Outer ring 3 ... Rolling body 4 ... Cage 6 ... Inner ring extension part 7 ... Spacer 8 ... Inner ring circumferential groove 9 ... Oil supply path 10 ... Oil discharge port 11 ... Depression part 12, 14 ... Opening peripheral part 18 ... Refueling port Br ... Rolling bearing Ku ... Supply / discharge oil mechanism δ1 ... Diameter clearance

Claims (11)

A rolling bearing in which a plurality of rolling elements held by a cage are interposed between the raceway surfaces of the inner and outer rings, and a supply / exhaust oil mechanism that supplies lubricating oil also serving as a bearing cooling medium into the bearing and discharges it outside the bearing. In a rolling bearing device with
An inner ring extension extending in the axial direction is provided on the inner ring, and a spacer adjacent to the outer ring and having an inner peripheral surface facing the inner ring extension is provided.
The oil supply / discharge oil mechanism is
An inner ring circumferential groove provided on the outer circumferential surface of the inner ring extension,
An oil supply passage provided in the spacer and having an oil supply port for discharging the lubricating oil toward the inner ring circumferential groove;
A radial clearance that is provided between the outer peripheral surface of the inner ring extension portion on the bearing side of the inner ring circumferential groove and the inner peripheral surface of the spacer, and guides lubricating oil into the bearing;
Provided in the spacer, and communicated with the inner ring circumferential groove at a circumferential position different from the oil supply port, and has an oil discharge port for discharging lubricating oil,
2. A rolling bearing device according to claim 1, wherein a recess is provided on an inner peripheral surface of the spacer so as to collect lubricating oil supplied from the oil supply port and rebounded from the inner ring circumferential groove so as to face the inner ring circumferential groove.   The rolling bearing device according to claim 1, wherein the recessed portion includes a circumferential groove provided on an inner peripheral surface of the spacer.   In Claim 2, the axial position of the opening peripheral edge part connected to the radial clearance among the recesses is matched with the axial position of the opening peripheral edge connected to the radial clearance of the inner ring circumferential groove, and A rolling bearing device in which the width dimension of the recess and the inner ring circumferential groove is the same.   4. The rolling bearing device according to claim 2 or 3, wherein the recess becomes narrower toward the bottom surface.   4. The recess according to claim 2, wherein the recess has a circumferential groove provided on an inner circumferential surface of the spacer and a circumferential width that is connected to a lower portion of the circumferential groove and has a larger width than the circumferential groove. A rolling bearing device having a groove.   The rolling bearing device according to any one of claims 2 to 5, wherein an oil drain port of the spacer is provided in a tangential direction connected to a circumferential groove of the spacer.   The rolling bearing device according to claim 1, wherein the recess is provided in an arc shape extending from an oil supply port of the spacer to an oil discharge port.   The rolling bearing device according to any one of claims 1 to 7, wherein the inner ring circumferential groove has oil repellency.   In any 1 item | term of Claim 1 thru | or 8, It becomes so that it may become a large diameter as it goes to the said track surface side between the inner ring track surface and the part which forms the said radial clearance among the outer peripheral surfaces of the said inner ring. A rolling bearing device provided with an inclined surface formed in a cross-sectional shape inclined to the surface.   The rolling bearing device according to claim 1, wherein the rolling bearing is an angular ball bearing.   11. The rolling bearing device according to claim 1, wherein the rolling bearing device is used for supporting a machine tool spindle.

Images