JP2008151180A - Lubrication device for rolling bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a lubrication device for a rolling bearing inhibiting power loss by increasing cooling efficiency of an inner ring and making inner and outer ring temperature difference as small as possible, and making mixing resistance of lubricating oil low. <P>SOLUTION: A lubricating oil introduction member 7 includes a nozzle 10 opening toward an end surface side of an inner ring 3 of the rolling bearing 2 and delivering lubricating oil to the inner ring 3, and a flange part 12 positioned on an outer diameter side from the nozzle 10 and covering an outer circumference of the inner ring 3. The inner ring 3 includes a circumference groove 9 opposing to a section where the nozzle 10 is provided and opening along an axial direction from an end surface of the inner ring 3. An axial position of a groove bottom 9b of the circumference groove 9 is set near a raceway surface 3a of the inner ring 3. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a lubrication device for a rolling bearing that is applied to, for example, an angular ball bearing for a machine tool main shaft and rotates at an ultra-high speed, and more particularly to a technique that is applied to the specifications of a fixed position preloading system and a rear combination.

Machine tool spindles tend to increase in speed in order to increase machining efficiency. As the spindle speed increases, torque and heat generation in the spindle device increase. Various lubrication devices for coping with this have been proposed and put into practical use (see Patent Documents 1 and 2).
FIG. 6 shows a bearing device using the technique of Patent Document 1. The inner ring 80 of this bearing is formed with a circumferential groove 80a (so-called scoop groove) for cooling the inner ring 80 by jet lubrication. In the thing of patent document 2, an inner ring end surface is shortened to such an extent that it does not have a bad influence on driving | operation (it shortens in an axial direction), and lubricating oil is injected from the nozzle spacer toward the inner ring end surface.

JP 2006-118525 A Japanese Patent No. 2740304

In Patent Document 1, since the bottom surface of the scoop groove of the inner ring and the contact position between the inner ring, which is a heating element, and the rolling element are separated from each other, cooling with the lubricating oil is performed from the separated position, thereby cooling the inner ring. Will fall. When a bearing for a machine tool is operated, the temperature rise of the inner ring becomes larger than that of the outer ring, and the temperature difference between the inner and outer rings becomes larger. As described above, when the cooling efficiency of the inner ring decreases, it becomes difficult to eliminate the increase in the temperature difference between the inner and outer rings. In the fixed position preload method, there is a possibility that an excessive preload may occur due to the temperature difference between the inner and outer rings.
In Patent Document 2, the inner ring can be effectively cooled. However, when the technique according to Patent Document 2 is used for jet lubrication, a large amount of oil enters the bearing, resulting in power loss and lubrication oil stirring resistance. Increase.

  SUMMARY OF THE INVENTION An object of the present invention is to provide a rolling bearing lubrication device that can increase the cooling efficiency of the inner ring to reduce the temperature difference between the inner and outer rings as much as possible, suppress power loss, and reduce the stirring resistance of the lubricating oil. is there.

  The lubrication device for a rolling bearing according to the present invention is a lubrication device for a rolling bearing in which the lubricating oil is discharged from the lubricating oil introduction member into the rolling bearing and lubricated. And a discharge port for discharging the lubricating oil to the inner ring, and a hook-like portion that is positioned on the outer diameter side of the discharge port and covers the outer periphery of the inner ring, and the inner ring is a lubricating oil introduction member Opposite to the location where the discharge port is provided, has a circumferential groove that opens in the axial direction from the end face of the inner ring, and the axial position of the groove bottom of the circumferential groove is the raceway surface of the inner ring. It is located in the vicinity.

  According to this configuration, the lubricating oil discharged from the discharge port of the lubricating oil introduction member to the end surface of the inner ring is collected in the circumferential groove. Part of the collected lubricating oil is guided between the outer periphery of the inner ring and the hook-shaped portion covering the outer periphery by centrifugal force and surface tension acting by the rotation of the inner ring, and is supplied to the raceway surface. The As described above, since the lubricant discharged from the lubricant introduction member is supplied to the raceway surface from between the outer periphery of the inner ring and the bowl-shaped portion, a large amount of lubricant does not enter the bearing. Since the stirring resistance of the lubricating oil can be reduced, no large power loss occurs. Therefore, high speed operation is possible without increasing power loss.

  Further, since the lubricating oil discharged from the discharge port is collected and discharged in the circumferential groove as described above, the inner ring is cooled by the lubricating oil collected in the circumferential groove. In this case, since the axial position of the groove bottom of the circumferential groove is positioned in the vicinity of the raceway surface of the inner ring, the groove bottom of the circumferential groove is brought close to the contact position between the inner ring that is the heat generating portion and the rolling element. be able to. Therefore, the cooling with the lubricating oil can be performed near the heat generating portion, the efficiency of heat conduction is hardly reduced, and the cooling efficiency of the inner ring that generates heat by the operation of the bearing can be increased. As a result, during bearing operation, the temperature increase of the inner ring relative to the outer ring can be suppressed as much as possible, and the temperature difference between the inner and outer rings can be minimized. When this bearing is used in a fixed position preload system, it is possible to prevent an excessive preload due to the temperature difference between the inner and outer rings.

  In the present invention, the rolling bearing is an angular ball bearing, and is an inclined surface portion having a diameter that increases from the end surface side of the inner ring toward the raceway surface side at the outer diameter portion of the inner ring, and a gap is formed in the flange portion. And the axial position of the groove bottom of the circumferential groove is a first axis that is the position of the intersection of the slope and the raceway surface in the vicinity of the raceway surface of the inner ring. It is preferable to be located in a range from the direction position to a second axial position that is a position forming a contact angle with the rolling element in the raceway surface. According to this configuration, the axial position of the groove bottom of the circumferential groove is defined based on the slope portion, the raceway surface, and the position that forms the contact angle with the rolling element among the raceway surfaces. As a result, cooling with the lubricating oil can be performed in the vicinity of the contact portion between the raceway surface and the rolling element, which is the main heat generating part, and the cooling efficiency of the inner ring that generates heat by the operation of the bearing can be significantly and reliably increased.

  In this invention, it is preferable that the rolling bearing is used at a fixed position preload. According to this configuration, during the operation of the bearing, it is possible to prevent an excessive preload caused by the inner and outer ring temperature differences from occurring and maintain an appropriate preload.

  According to the rolling bearing lubrication device of the present invention, since the lubricating oil is supplied to the raceway surface from between the outer periphery of the inner ring and the bowl-shaped portion, a large amount of lubricating oil does not enter the bearing, Since the stirring resistance of the lubricating oil can be reduced, a large power loss does not occur. Further, since the axial position of the groove bottom of the circumferential groove is positioned in the vicinity of the raceway surface of the inner ring, the cooling efficiency of the inner ring can be enhanced. When this bearing is used in a fixed position preload system, it is possible to prevent an excessive preload due to the temperature difference between the inner and outer rings.

A first embodiment of the present invention will be described with reference to FIGS. The first embodiment is applied to a multi-row rolling bearing device for a machine tool spindle. In this multi-row rolling bearing device 1, for example, a plurality (two in this case) of angular ball bearings are arranged in a rear combination. Each rolling bearing 2 has a plurality of rolling elements 5 made of balls interposed between raceway surfaces 3 a and 4 a of the inner ring 3 and the outer ring 4, and each rolling element 5 is held by a cage 6.
A pair of lubricating oil introduction members 7 are interposed between the outer rings 4 and 4 of the adjacent rolling bearings 2 and 2. Each lubricating oil introduction member 7 discharges cooling oil and supplies a part thereof into the corresponding rolling bearing 2. An inner ring spacer 8 is interposed between the inner rings 3 and 3.

  The cage 6 is an outer ring guide type, and the material thereof is preferably phenol resin, PEEK, PPS, polyamide resin, C / C composite, aluminum alloy, Ti alloy (strength improvement at high speed). The material of the inner ring 3 is, for example, carburized steel in consideration of a large fitting hoop stress at high speed. However, it is not limited to carburized steel. The rolling element 5 is preferably made of ceramic from the viewpoint of reducing centrifugal force.

A circumferential groove 9 that is recessed in the axial direction is formed on the width surface (end surface) of the inner ring 3 on the side opposite to the load of each rolling bearing 2, that is, the bearing back side. The outer diameter surface following the raceway surface on the side where the circumferential groove 9 of the inner ring 3 is formed is a slope portion 3b having a larger diameter on the raceway surface side. That is, the outer diameter surface of the portion where the step surface of the inner ring 3 is provided is the slope portion 3b.
The lubricant introduction member 7 is a ring-shaped outer ring spacer provided adjacent to the rolling bearing 2 in the axial direction by contacting the corresponding width surface (end surface) of the outer ring 4. The lubricating oil introduction member 7 includes a nozzle (corresponding to a discharge port) 10 that opens to face the end surface of the inner ring 3 where the circumferential groove 9 is provided, and an oil supply path 11 that communicates with the nozzle 10. And a hook-like portion 12 is provided. The cooling oil supplied to the oil supply passage 11 and discharged from the nozzle 10 is blown to the circumferential groove 9 of the inner ring 3, and a part of the cooling oil is inclined from the outer diameter surface 9 a of the circumferential groove 9 by centrifugal force and surface tension. It flows as lubricating oil to the raceway surface 3a of the inner ring 3 along the portion 3b. The hook-shaped portion 12 extends in the axial direction from the side surface of the lubricating oil introduction member 7 toward the corresponding bearing 2 and covers the inclined surface portion 3b of the inner ring 3 via a gap (micro gap) δ. The lubricating oil flowing to the raceway surface 3a is guided. The hook-shaped portion 12 extends to the inner diameter side of the cage 6.

In the inner ring 3, an annular corner 3ba where the outer diameter surface 9a of the circumferential groove 9 and the inclined surface portion 3b intersect is a curved surface portion having an arcuate cross section. By making the corner portion 3ba a curved surface portion having an arcuate cross section, the lubricating oil is prevented from leaving the inner ring 3 by centrifugal force from this corner portion 3ba (does not contribute to lubrication of the raceway surface 3a). .
The circumferential groove 9 of the inner ring 3 forms a bottomed annular groove, and the groove bottom 9b has a bottom surface perpendicular to the axis. However, the groove bottom 9b is not limited to the bottom surface perpendicular to the axis. In particular, the axial position of the groove bottom 9 b is located in the vicinity of the raceway surface 3 a of the inner ring 3. Specifically, the axial position of the groove bottom 9b of the circumferential groove 9 is determined from the axial position P1, which is the position of the intersection of the inclined surface portion 3b and the track surface 3a, in the vicinity of the track surface 3a of the inner ring 3. It is located in the range (refer FIG. 2) to the axial direction position P2 which is a position which makes the minimum diameter among the surfaces 3a.

  An outer diameter surface 9a of the circumferential groove 9 (that is, a circumferential surface facing inward in the radial direction and positioned at an outer diameter from an inner diameter surface 9c of the circumferential groove 9 described later) is a nozzle position, an inclination angle of the nozzle 10 (axis For example, the diameter is defined to be slightly smaller than the minimum diameter of the raceway surface 3a of the inner ring 3. The inner diameter surface 9c of the circumferential groove 9 is, for example, between the diameter d1 of the raceway surface 3a of the inner ring 3 and the inner ring inner diameter d2 based on the nozzle position, the inclination angle of the nozzle 10, and at least the outer ring surface 9c. The diameter is defined to be smaller than the diameter surface 9a. Further, the inner diameter surface 9 c of the circumferential groove 9 is defined to be slightly smaller than the outer diameter surface 8 a of the inner ring spacer 8. As described above, the axial position of the groove bottom 9b of the circumferential groove 9 is defined, and the outer diameter surface 9a and the inner diameter surface 9c of the circumferential groove 9 are also defined, so that the rigidity of the inner ring 3 is ensured. In addition, the cooling efficiency of the inner ring 3 can be increased.

On the side surfaces of the lubricating oil introduction members 7 that are in contact with each other, there are formed oil drain recesses 13 that open to the inner periphery, and the inner surfaces of these oil drain recesses 13 and 13 and the inner ring spacer 8. The space surrounded by the outer diameter surface 8a is an oil drainage space 14. The oil discharge space 14 is communicated with a space 15 in which the lubricating oil discharged from the nozzle 10 in the rolling bearings 2 and 2 on both sides is discharged.
Further, groove-like oil drain passages 16 extending in the radial direction from the oil drain recess 13 toward the outer peripheral side are formed on the side surfaces of the lubricating oil introduction members 7 that are in contact with each other. In addition, it is desirable that the lubricating oil introducing member 7 is subjected to a quenching treatment from the viewpoint of preventing the occurrence of scratches and improving the handleability.

  Of the lubricating oil discharged from the nozzle 10, the remaining lubricating oil excluding the inflow flowing into the minute gap δ is discharged to the outside from the lubricating oil discharge path 17. The lubricating oil discharge path 17 is configured by an oil draining space 14 formed by a draining recess 13 formed in both the lubricating oil introduction members 7, the groove-shaped draining paths 16 and 18, and the like. Note that a plurality of the groove-like oil drain passages 16 and 18 may be provided in the circumferential direction. As the cooling oil to be used, the viscosity of ISO is preferably VG10 or VG2 or less from the viewpoint of reducing power loss and improving cooling efficiency. Further, for further reduction of power loss and improvement of cooling efficiency, use of water-soluble hydraulic oil having low viscosity and high thermal conductivity as cooling oil, and stainless steel having a low coefficient of linear expansion as the material of the lubricating oil introduction member 7 are used. It is desirable to use steel.

The lubricating action of the multi-row rolling bearing device 1 will be described.
The cooling oil pumped to the oil supply passage 11 of each lubricating oil introduction member 7 is discharged from the nozzle 10 and sprayed to the formation location of the circumferential groove 9 of the inner ring 3 facing. A part of the cooling oil sprayed on the circumferential groove 9 is caused by the surface tension and the inner wall surface on the outer diameter side of the circumferential groove 9 in the inner ring 3 due to the centrifugal force acting on the cooling oil as the inner ring 3 rotates. To the raceway surface 3a of the inner ring 3 along the slope 3b. In this way, the cooling oil discharged from the nozzle 10 is collected in the circumferential groove 9, and a part thereof flows from the slope portion 3b of the inner ring 3 to the raceway surface 3a, so that the entire circumference of the raceway surface 3a is evenly lubricated. Oil can be supplied. The lubricating oil is smoothly moved from the inner wall of the circumferential groove 9 to the inclined surface portion 3b by appropriately balancing the surface tension of the lubricating oil, the centrifugal force acting on the lubricating oil, and the inclination angle of the inclined surface portion 3b. It is possible to prevent the lubricating oil from being scattered by centrifugal force. Here, in the inner ring 3, the annular corner 3ba where the outer diameter surface 9a of the circumferential groove 9 and the inclined surface portion 3b intersect is a curved surface portion having an arcuate cross section. The oil is prevented from being separated from the inner ring 3 by centrifugal force, and the lubricating oil is moved more smoothly to the slope portion 3b.

The inclined surface portion 3b of the inner ring 3 is covered with the flange portion 12 of the lubricating oil introducing member 7 through a gap δ, and the lubricating oil flowing from the gap δ to the raceway surface 3a is guided by the flange portion 12. The lubricating oil flowing in the gap δ is pressed against the inner diameter surface side of the bowl-shaped portion 12 by the action of centrifugal force without being flowed to the inclined surface portion 3b due to various conditions such as rotational speed and inclination angle. May flow in. The lubricating oil that flows in this state falls off to the outer diameter side by centrifugal force at a location where the tip of the bowl-shaped portion 12 is exited. However, since the hook-shaped portion 12 extends to the inner diameter side of the cage 6, the lubricating oil that has flowed down from the tip of the cage-shaped portion 12 to the outer diameter side is received by the inner diameter surface of the cage 6, and the rolling element 5. Will be supplied to. For this reason, the lubricating oil supplied to the gap δ between the slope portion 3b of the inner ring 3 and the flange portion 12 of the lubricating oil introducing member 7 is used for lubrication without waste.
When the gap δ is a minute gap narrower than the oil film of the lubricating oil flowing along the inclined surface portion 3b, the flow rate can be adjusted by this gap, so the flow rate of the cooling oil to the oil supply passage 11 is adjusted from the outside. Without this, the flow rate of the lubricating oil flowing through the minute gap can be easily adjusted.

  The remaining lubricating oil excluding the inflow flowing into the minute gap δ is the inner diameter of the oil drain recesses 13 and 13 and the outer diameter of the inner ring spacer 8 of each lubricating oil introduction member 7 constituting the lubricating oil discharge path 17. The oil is discharged to the outside by an oil discharge pump (not shown) through the oil discharge space 14 surrounded by the surface 8a and the groove oil discharge passages 16 and 18 of each lubricating oil introduction member 7. The multi-row rolling bearing device 1 is effectively cooled by the lubricating oil as the cooling oil discharged through such a path.

  According to the first embodiment described above, the lubricating oil discharged from the nozzle 10 of the lubricating oil introducing member 7 is collected in the circumferential groove 9. A part of the collected lubricating oil is guided between the outer periphery of the inner ring 3 and the hook-shaped portion 12 covering the outer periphery by centrifugal force and surface tension acting by the rotation of the inner ring 3, and the raceway surface. 3a. Thus, since the lubricant discharged from the lubricant introduction member 7 is supplied to the raceway surface 3a from between the outer periphery of the inner ring 3 and the flange-shaped portion 12, a large amount of lubricant is contained in the bearing 2. Since it does not penetrate and the stirring resistance of the lubricating oil can be reduced, a large power loss does not occur. Therefore, high speed operation is possible without increasing power loss.

  Further, since the lubricating oil discharged from the nozzle 10 is collected and discharged in the circumferential groove 9 as described above, the inner ring 3 is cooled by the lubricating oil collected in the circumferential groove 9. In this case, since the axial position of the groove bottom 9b of the circumferential groove 9 is positioned in the vicinity of the raceway surface 3a of the inner ring 3, the groove bottom 9b of the circumferential groove 9 is rotated with the inner ring 3 that is a heat generating portion. The position of contact with the moving body 5 can be approached. Therefore, the cooling with the lubricating oil can be performed near the heat generating portion, the efficiency of the heat conduction is reduced, and the cooling efficiency of the inner ring 3 that generates heat by the operation of the bearing 2 can be increased. As a result, during the bearing operation, it is possible to suppress the temperature rise of the inner ring 3 relative to the outer ring 4 as much as possible, and to reduce the temperature difference between the inner and outer rings as much as possible. When this bearing 2 is used in a fixed position preload system, it is possible to prevent an excessive preload caused by the temperature difference between the inner and outer rings. That is, an appropriate preload can be maintained during operation of the bearing 2.

  Since the inner diameter surface 9c of the circumferential groove 9 is defined to be slightly smaller than the outer diameter surface 8a of the inner ring spacer 8, the lubricating oil discharged from the nozzle 10 is smoothly blocked without being blocked by the inner ring end surface. It is introduced into this circumferential groove 9. As described above, the diameter dimensions of the outer diameter surface 9a and the inner diameter surface 9c of the circumferential groove 9 are defined based on the nozzle position, the inclination angle of the nozzle 10, and the like, while ensuring the rigidity and strength of the inner ring 3, and cooling oil It is possible to secure a necessary and sufficient volume for collecting oil. By positioning the axial position of the groove bottom 9b of the circumferential groove 9 in the vicinity of the raceway surface 3a of the inner ring 3, the inner ring 3 can be made lighter than that of the prior art. Therefore, the starting torque for rotating the inner ring 3 and the like can be kept low, and for example, the motor that rotationally drives the main shaft can have a low rated output. Therefore, the manufacturing cost can be reduced. In addition, when the groove bottom 9b of the circumferential groove 9 is formed in a shape that becomes sharper toward the other end surface rather than a bottom surface perpendicular to the axial direction, the axial position and radial position of the groove bottom are further increased. It is possible to approach the track surface 3a. In this case, the cooling efficiency of the inner ring that generates heat by the operation of the bearing can be further increased.

  FIG. 4 shows an example of a spindle device provided with the multi-row rolling bearing device 1 of the embodiment shown in FIG. The spindle device 19 is applied to a machine tool, and a tool or workpiece chuck is attached to the tip of the main shaft 20 (the left end in the figure). The main shaft 20 is supported by a plurality (here, two) of multi-row rolling bearing devices 1 separated in the axial direction. In these multi-row rolling bearing devices 1, the rolling bearings 2 and 2 adjacent to each other with the lubricating oil introduction member 7 interposed therebetween are combined with the back surface and are used in a fixed position preload.

  The inner ring 3 of each rolling bearing 2 in each multi-row rolling bearing 1 is fitted to the outer diameter surface of the main shaft 20, and the outer ring 4 is fitted to the inner diameter surface of the housing 21. A motor 22 for driving the main shaft 20 is arranged at an intermediate position in the axial direction between the multi-row rolling bearing devices 1 and 1 in the housing 21. The motor rotor 23 is fixed to the main shaft 20, and the motor stator 24 is fixed to the housing 21.

  Inner and outer rings 3, 4 of the rolling bearing 2 positioned on the spindle shaft end side in each multi-row rolling bearing 1 are respectively provided with step portions 20 a, 21 a facing the axial direction of the main shaft 20 and the housing 21 by inner ring retainers 25 and outer ring retainers 26. It is fixed in a state of being sandwiched between. At one end portion of the main shaft 20, a bearing fixing nut 27 that is pressed against the inner ring presser 25 and fixes the multi-row rolling bearing device 1 is screwed. The main shaft 20 and the stepped portions 20a and 21a of the housing 21 and the positions of the bearing contact surfaces of the inner ring retainer 25 and the outer ring retainer 26 are set to predetermined positions, and two bearing fixing nuts 27 are tightened to align the two. The rolling bearing 2 is preloaded at a fixed position.

  The housing 21 has a double structure including an inner peripheral housing 21A and an outer peripheral housing 21B. The inner peripheral housing 21A is provided with a lubricating oil supply path 28 communicating with the oil supply path 11 of each lubricating oil introduction member 7, a drain oil recovery path 29, and a housing cooling oil supply path (not shown). Yes. Each lubricating oil supply path 28 extends in the axial direction and opens at both end faces of the inner peripheral housing 21A. The oil recovery path 29 extends in the axial direction and opens at both end faces of the inner peripheral housing 21A. Lubricating oil discharge paths 17 (FIG. 3) of the respective lubricating oil introduction members 7 are communicated with the drain oil recovery path 29.

  The waste oil that has flowed out to the waste oil recovery passage 29 is recovered in an oil recovery tank by a waste oil pump and returned to a cooling oil supply device (none of which is shown), and the oil supply passage 11 is returned from this cooling oil supply device. The cooling oil is supplied again. Further, the cooling oil is also supplied from the cooling oil supply device to the oil supply passage 11, and the housing 21 is cooled. The cooling oil that has cooled the housing 21 is recovered in the oil recovery tank and returned to the cooling oil supply device again.

  Next, a second embodiment of the present invention will be described with reference to FIG. However, the same components as those in the first embodiment shown in FIG. 1 to FIG. Also in the second embodiment, angular ball bearings are employed. On the outer diameter portion of the inner ring 3A, there is a slope portion 3b that increases in diameter from the end surface side toward the raceway surface 3a side, and is disposed in the flange-like portion 12 of the lubricating oil introduction member 7 via a gap δ. A slope portion 3b is provided.

  The axial position of the groove bottom 9Ab of the circumferential groove 9A of the inner ring 3A is the first axial position P1 that is the position of the intersection of the inclined surface portion 3b and the track surface 3a in the vicinity of the track surface 3a of the inner ring 3A. To the second axial position PAx that is the position that forms the contact angle Ax with the rolling element 5 in the raceway surface 3a. Based on the position of the inclined surface 3b, the raceway surface 3a, and the raceway surface 3a that forms the contact angle Ax with the rolling element 5, the first and second axial positions P1, of the groove bottom 9Ab of the circumferential groove 9A PAx is defined.

  In the angular ball bearing, in the inner ring 3A, the opening of the circumferential groove 9A is not an end face (width surface on the right side of the drawing) adjacent to the part forming the contact angle Ax with the rolling element 5, but the part forming the contact angle Ax It formed in the end surface (width surface of the left side of a figure) separated from. As a result, the axial position of the groove bottom 9Ab of the circumferential groove 9A can be deeply reached to the second axial position PAx that is the position that forms the contact angle Ax with the rolling element 5 in the raceway surface 3a. Thereby, the cooling efficiency of the inner ring 3A that generates heat by the operation of the bearing can be remarkably increased. Other effects similar to those of the first embodiment are obtained.

It is sectional drawing which shows the lubricating device of the rolling bearing which concerns on the 1st Embodiment of this invention. It is a principal part enlarged view of the inner ring | wheel etc. in FIG. It is sectional drawing which shows an example which combined the rolling bearing with the back surface combination. It is sectional drawing which shows the spindle apparatus provided with the rolling bearing. It is an expanded sectional view of an inner ring etc. of a rolling bearing concerning a 2nd embodiment of the present invention. It is sectional drawing which shows the lubricating device of the conventional rolling bearing.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Multi row rolling bearing apparatus 3 ... Inner ring 3a ... Raceway surface 3b ... Slope part 7 ... Lubricating oil introduction member 9 ... Circumferential groove 10 ... Nozzle 12 ... Gutter-like part delta ... Gap P1 ... 1st axial position PAx ... Second axial position

Claims (3)

In a rolling bearing lubrication device that discharges and lubricates lubricating oil from a lubricating oil introducing member into the rolling bearing,
The lubricating oil introduction member opens opposite to the end face side of the inner ring of the rolling bearing, and is disposed on the outer periphery of the inner ring, located on the outer diameter side of the discharge port that discharges the lubricating oil to the inner ring, and the discharge port. Has a bowl-shaped part to cover,
The inner ring has a circumferential groove that opens along the axial direction from the end surface of the inner ring so as to face a portion where the discharge port of the lubricating oil introduction member is provided, and the axial direction of the groove bottom of the circumferential groove A lubricating device for a rolling bearing, wherein the position is located in the vicinity of a raceway surface of the inner ring. In claim 1,
The rolling bearing is an angular ball bearing, and is an inclined surface portion having a diameter increasing toward an outer diameter portion of the inner ring from the end surface side of the inner ring toward the raceway surface side. Provided a sloped part,
The axial position of the groove bottom of the circumferential groove is from the first axial position, which is the position of the intersection of the slope portion and the raceway surface, in the vicinity of the raceway surface of the inner ring, and the rolling element of the raceway surface. The rolling bearing lubrication device is located in a range up to a second axial position, which is a position that forms the contact angle.   3. The lubricating device for a rolling bearing according to claim 1, wherein the rolling bearing is used with a fixed position preload.

Images