JP2008089171A - Rolling bearing lubricating device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rolling bearing lubricating device for supplying lubricating oil as well as cooling a bearing, suppressing a cooling distribution difference in the axial direction of the raceway surface of an inner ring, and efficiently contributing to equally cooling the delivered lubricating oil, while improving the lubrication of the end faces of rollers when applied to a cylindrical roller bearing. <P>SOLUTION: A circumferential groove 6 is provided in the end face of the inner ring 2 of the rolling bearing 1 such as the cylindrical roller bearing, and a nozzle 8 for delivering lubricating oil into the circumferential groove 6 is provided in a lubricating oil introduction member 7 located adjacent to an outer ring 3 of the rolling bearing 1. Axial through-holes 52 passing from the bottom face of the circumferential groove 6 through the inner ring 2 in the axial direction for the lubricating oil in the circumferential groove 6 to move therethrough is provided in a plurality of circumferential positions. Lubricating oil holes 54 are provided branching from the axial through-holes 52 in communication with an abrading take-off 53. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a rolling bearing lubrication device used for supporting a high-speed spindle such as a spindle for a machine tool.

Machine tool spindles tend to increase in speed in order to increase machining efficiency. As the speed of the main shaft increases, air-oil lubrication is often used for lubricating the main shaft bearing, in which lubricating oil is mixed into the conveying air and the oil is injected into the bearing from the nozzle.
Since general air-oil lubrication requires a large amount of high-pressure air and generates a large amount of noise, an improved air-oil lubrication structure has been proposed for the purpose of low noise, energy saving, and resource saving (for example, Patent Document 1). The air-oil lubrication structure disclosed in Patent Document 1 is provided with a slope portion on the outer diameter surface of an inner ring of a rolling bearing, and a nozzle member along which a lubricant oil inflow gap is provided on the slope portion.

  Air-oil lubrication is not limited to general air-oil lubrication, and even with an improved air-oil lubrication structure as disclosed in Patent Document 1, the cooling effect of the bearing is small, and the temperature difference between the inner and outer rings (inner ring)> ( This has the disadvantage of causing excessive preload due to the outer ring.

  As a lubrication method to keep the temperature rise of the bearing small, there is jet lubrication that injects a large amount of oil into the bearing and lubricates and cools the bearing at the same time, but the power loss increases due to the stirring resistance by the oil that entered the bearing There are drawbacks.

  For this reason, a new jet lubrication structure has also been proposed in which heat generation is reduced by jet lubrication and the amount of lubricating oil entering the bearing is limited to reduce the agitation resistance due to oil (for example, Patent Document 2).

  The new jet lubrication structure disclosed in Patent Document 2 cools the inner ring heat generation by receiving the lubricating oil discharged from the lubricating oil introducing member composed of the outer ring side spacer or the like by a circumferential groove provided on the end face of the inner ring. It is. Most of the cooled lubricating oil is discharged to the outside of the bearing, but a small amount of the lubricating oil is used for bearing lubrication from the lubricating oil inflow gap provided between the lubricating oil introducing member and the outer diameter slope of the inner ring. Flow into. As a result, only a small amount of lubricating oil enters the bearing, the stirring resistance is reduced, and the driving torque of the main shaft is also reduced.

Conventionally, as a lubricating device for lubricating and cooling the bearing, axial through holes are provided at a plurality of locations in the circumferential direction of the inner ring, and lubrication is performed toward the through hole of the inner ring separately from the bearing lubricating nozzle. A nozzle provided with a nozzle for discharging oil has been proposed (for example, Patent Document 3).
JP 2002-61657 A JP 2005-180703 A Japanese Utility Model Publication No. 4-90722

  The new jet lubrication structure disclosed in Patent Document 2 is an excellent lubrication structure in that it can perform cooling and micro lubrication. However, since cooling is performed from only one side of the inner ring, the left and right cooling is uneven, and the bearing function is improved. , Proper cooling may not be possible. In particular, when applied to a cylindrical roller bearing, the problem due to uneven cooling is large.

  The above-described new jet lubrication structure is as shown in FIG. 11 when applied to a cylindrical roller bearing. That is, the lubricating oil discharged from the lubricating oil introducing member 7D is received by the circumferential groove 6 provided on the end face of the inner ring 2 to cool the heat generation of the inner ring 2. Most of the cooled lubricating oil is discharged out of the bearing, but a small amount is used for lubricating the bearing between the flange-shaped protrusion 7Da provided on the lubricating oil introducing member 7 and the outer diameter inclined surface 2c of the inner ring 2. It flows into the raceway surface of the inner ring 2 from the lubricating oil inflow gap δ.

  Since Patent Document 2 is applied to an angular ball bearing, and the raceway surface and the rolling element are in point contact, even if the left and right are unevenly cooled, there is not much trouble. However, when applied to a cylindrical roller bearing as shown in FIG. 11, the cylindrical roller 4 as a rolling element and the raceway surface 2a of the inner ring 2 are in line contact. Therefore, when the inner ring 2 is cooled unevenly on the left and right, there is a concern about the influence on the surface pressure distribution of the cylindrical roller 4 due to the difference in outer diameter due to the difference in thermal expansion between the left and right portions of the raceway surface 2a. The uneven distribution of surface pressure leads to an early life.

  Further, in the case of a cylindrical roller bearing, the flange 2b of the inner ring 2 and the end surface of the cylindrical roller 4 rotate while being in contact with each other due to skew or the like, and are in sliding contact. For this reason, there is a risk that lubrication will be insufficient with the above-described new jet method.

  In addition, as in Patent Document 3, in which an axial through hole is provided at a plurality of locations in the circumferential direction of the inner ring and nozzles that discharge toward the through hole are provided, the inner ring that rotates from the nozzle at the stationary position Since the lubricating oil is discharged to the through hole in the end face, the discharged lubricating oil is discharged without entering the through hole, and it is difficult to perform efficient cooling.

The object of the present invention is to supply lubricating oil that also serves to cool the bearing, to suppress the difference in cooling distribution in the axial direction of the inner ring raceway surface, and to efficiently contribute to the uniform cooling of the discharged lubricating oil. It is an object to provide a rolling bearing lubrication device capable of supporting the above.
Another object of the present invention is to improve the lubrication of the roller end face when applied to a cylindrical roller bearing.
Still another object of the present invention is to cool the inner ring even more efficiently.

  In the rolling bearing lubrication device of the present invention, a circumferential groove is provided on an end surface of the inner ring of the rolling bearing, and a nozzle that discharges lubricating oil that also serves as a bearing cooling medium is provided in the circumferential groove adjacent to the outer ring of the rolling bearing. Provided in a lubricating oil introducing member, and provided with axial through holes at a plurality of positions in the circumferential direction through the inner ring in the axial direction from the bottom surface of the circumferential groove and allowing the lubricating oil in the circumferential groove to pass therethrough. Features.

  According to this configuration, the lubricating oil discharged from the nozzle is received by the circumferential groove on the inner ring end face, and cools the inner ring from the end face. A part of the lubricating oil received in the circumferential groove is discharged from the circumferential groove to the outer diameter side, and part or all of it flows into the bearing. As a result, the lubricating oil can be supplied also for cooling the bearing. The remaining part of the lubricating oil received in the circumferential groove passes through the axial through-holes provided at a plurality of locations in the circumferential direction of the inner ring, and the entire inner ring in the length direction of the axial through-hole is removed. Cooling. Therefore, the inner ring is uniformly cooled in the width direction, and the difference in cooling distribution in the inner ring raceway axis direction can be suppressed. Unlike the one provided in the end surface of the inner ring, the axial through hole is provided with the bottom surface of the circumferential groove on the end surface of the inner ring as an inlet, so that the lubricating oil discharged from the nozzle is temporarily accumulated in the circumferential groove. It efficiently flows into each axial through hole. Therefore, the lubricating oil discharged from the nozzle contributes efficiently to uniform cooling.

In this invention, when the rolling bearing is a cylindrical roller bearing with an inner ring rod, the lubricating oil supply holes respectively leading to the respective polishing thefts formed at the corners between the flange surface and the raceway surface on both sides of the inner ring, You may branch and provide from an axial direction through-hole.
In this way, when a lubricating oil supply hole that branches off from the axial through hole and leads to polishing theft is provided, the lubricating oil is supplied to the flange surface that is likely to be insufficiently lubricated due to sliding contact or skew, and the roller end surface is well lubricated. Done. Moreover, lubricating oil is also supplied to the raceway surface, so that insufficient lubrication can be avoided. Since the lubrication holes are provided in the polishing steals on both sides, the lubrication oil is supplied from one nozzle, and the left and right can be evenly lubricated. Since the lubrication oil hole is opened for polishing stealing, the problem of deterioration in durability of the cylindrical roller and the raceway surface due to the formation of the lubrication oil hole does not occur as compared with the case where the lubrication oil hole is opened on the raceway surface.

  Further, in the present invention, when the rolling bearing is a cylindrical roller bearing with an inner ring flange, a lubricating oil supply hole that leads to a polishing steal formed at a corner between the flange surface and the raceway surface of the inner ring is provided with the circumferential groove. May be provided. Even if the lubricating oil supply hole is opened from the circumferential groove, the lubricating oil can be supplied to the flange surface and the raceway surface.

Thus, when providing the lubricating oil supply hole opened from the axial through hole or the circumferential groove, it is preferable that the inner diameter of the lubricating oil supply hole is smaller than the inner diameter of the axial through hole.
Since the lubricating oil required for bearing lubrication is less than the lubricating oil required for cooling, reducing the inner diameter of the lubricating oil supply hole increases the flow of lubricating oil in the axial through-hole, enabling efficient cooling. .

In this invention, when the circumferential groove is inclined with respect to the axial direction so as to be located closer to the radial center as the distance from the end face of the inner ring increases, the axial through hole is connected to the bottom of the circumferential groove. It is assumed that the inlet side portion has the same inclination as the circumferential groove, is bent in the middle, and the outlet side portion has an inclination opposite to the inlet side portion and penetrates through the end face of the opposite inner ring. good.
If the inlet side portion of the axial through hole is made the same as the inclination of the circumferential groove, the lubricating oil in the circumferential groove tends to flow into the axial through hole. For this reason, the flow rate of the lubricating oil flowing through the axial through hole is increased, and the inner ring can be effectively cooled. In addition, the axial through hole is bent halfway, and the outlet side portion is inclined in the direction opposite to the inlet side portion to penetrate the end surface of the inner ring on the opposite side. Centrifugal force is generated by rotation of the inner ring in the part. For this reason, lubricating oil can be efficiently discharged | emitted from an axial direction through-hole.

  In the present invention, the rolling bearing may be used as a spindle bearing of a machine tool. The spindle of a machine tool has a tendency to increase the speed in order to increase the machining efficiency. On the other hand, it is important to prevent the thermal expansion of the spindle to improve the machining accuracy. For this reason, the effects of the lubricating oil supply that also serves to cool the bearing in the present invention and the stable and minute supply of the lubricating oil can be effectively exhibited.

In the rolling bearing lubrication device of the present invention, a circumferential groove is provided on an end surface of the inner ring of the rolling bearing, and a nozzle that discharges lubricating oil that also serves as a bearing cooling medium is provided in the circumferential groove adjacent to the outer ring of the rolling bearing. Provided in the lubricating oil introducing member, and through the inner ring from the bottom surface of the circumferential groove in the axial direction through the axial through holes through which the lubricating oil in the circumferential groove is passed, at a plurality of locations in the circumferential direction, Lubricating oil can be supplied also for cooling the bearing, a difference in cooling distribution in the axial direction of the inner raceway surface can be suppressed, and the discharged lubricating oil can be efficiently contributed to uniform cooling.
In particular, when the rolling bearing is a cylindrical roller bearing, the lubrication of the roller end surface is improved when a lubricating oil supply groove is provided from the axial through hole or the circumferential groove to lead to polishing stealing between the flange surface and the raceway surface. be able to.
The circumferential groove is inclined with respect to the axial direction so as to be located closer to the radial center as the distance from the end face of the inner ring increases, and the axial through hole is connected to the bottom of the circumferential groove. When the inner ring has the same inclination as the circumferential groove and is bent in the middle, the outlet side part is inclined in the direction opposite to the inlet side part and penetrates through the end surface of the opposite inner ring. Can be cooled more efficiently.

  A first embodiment of the present invention will be described with reference to FIGS. FIG. 1 shows a sectional view of a rolling bearing lubrication device of this embodiment. This rolling bearing lubrication device jets a large amount of lubricating oil from the lubricating oil introducing member 7 toward the rolling bearing 1 to simultaneously lubricate and cool the bearing. The rolling bearing 1 is used as a spindle bearing of a machine tool. As shown in an enlarged view in FIG. 2, the rolling bearing 1 is provided between the inner ring 2, the outer ring 3, and the raceway surfaces 2a and 3a of the inner and outer rings 2 and 3. It is a cylindrical roller bearing having a plurality of cylindrical rollers 4 which are interposed rolling elements. The cylindrical rollers 4 are held in respective pockets 5a provided in the cage 5 by an annular cage 5 at a predetermined interval in the circumferential direction. The outer ring 3 has no wrinkles and is fixed in a bearing box (not shown).

  The inner ring 2 is a hooked inner ring having hooks 2 b and 2 b on both sides of the raceway surface 2 a and is fitted to the outer diameter surface of the main shaft 25. A circumferential groove 6 is provided on one end face F <b> 1 of the inner ring 2. The circumferential groove 6 is formed from the end surface of the inner ring 2 to the outer diameter surface. The circumferential groove 6 is inclined in the axial direction so as to be located closer to the radial center as the distance from the end face F1 increases. The outer diameter surface of the inner ring 2 is provided with an outer diameter slope 2c that increases in diameter as it approaches the raceway surface 2a side from the end surface. Specifically, the outer diameter slope 2 c is provided on the outer diameter surface of the flange 2 b of the inner ring 2. Of the outer diameter surface of the flange 2b, the outer diameter inclined surface 2c is provided in such a range that the inner ring end surface side reaches the end edge and the inner surface side of the flange inner surface side remains in the end portion. The end face side having the circumferential groove 6 of the inner ring 2 is positioned by the inner ring spacer 21.

  The inner ring 2 has axial through holes 52 that pass through the inner ring 2 in the axial direction from the bottom surface of the circumferential groove 6 and allow the lubricating oil in the circumferential groove 6 to pass therethrough at a plurality of positions in the circumferential direction at equal intervals. Is provided. In these axial through holes 52, two lubricating oil supply holes 54 extending in the radial direction are branched. These lubricating oil supply holes 54 lead to both sides of the inner ring 2 to the respective polishing thefts 53 formed at the corners between the flange surface which is the inner surface of the flange 2b and the raceway surface 2a. The polishing steal 53 is a groove having an arcuate cross section provided so as not to hinder the polishing operation of the raceway surface 2a. The lubrication oil supply hole 54 has a smaller diameter than the axial through hole 52. The lubricating oil supply holes 54 may be provided in all of the plurality of axial through holes 52 provided, or may be provided only in some of the axial through holes 52.

The lubricating oil introducing member 7 is an outer ring positioning spacer that is disposed adjacent to the outer ring 3 on the end face side where the circumferential groove 6 of the inner ring 2 of the rolling bearing 1 is provided, and is fixed in the bearing box. The lubricant introduction member 7 is combined with a release lubricant regulation member 15.
The lubricating oil introduction member 7 is connected to the nozzle 8 for discharging the lubricating oil into the circumferential groove 6 of the inner ring 2 of the rolling bearing 1 and the nozzle 8 extending from the outer diameter surface of the lubricating oil introduction member 7 toward the inner diameter side. An oil supply passage 9 is formed. The nozzle 8 has an inclination angle at which the discharge port faces the axial center. In this embodiment, the circumferential groove 6 of the inner ring 2 is also inclined according to the inclination angle of the nozzle 8, but the circumferential groove 6 may be a groove perpendicular to the end face of the inner ring 2.

As shown in FIG. 3, a plurality of (for example, four) nozzles 8 of the lubricating oil introduction member 7 are provided in a distributed manner in the circumferential position of the lubricating oil introduction member 7. The lubricating oil introducing member 7 is composed of an annular main body 7a, a plurality of nozzle forming protrusions 7b protruding toward the inner diameter side at equal positions in the circumferential direction of the annular main body 7a, and an annular flange 7c. The nozzle 8 is provided on the protrusion 7b.
The oil supply passage 9 extends from the bottom surface of the oil supply passage C-shaped groove portion 9a provided on the outer diameter surface of the annular main body 7a to the inner diameter side at the circumferential position of each nozzle forming protrusion 7b. It consists of an oil supply passage individual hole 9b. The nozzle 8 communicates with the tip of the oil supply passage individual hole 9b.

  The annular flange portion 7c has an inner diameter surface at the tip that is formed on an inner diameter slope 7ca that faces the outer diameter slope 2c of the inner ring 2 via a lubricating oil inflow gap δ. The inner diameter slope 7ca is parallel to the outer diameter slope 2c of the inner ring 2, and the lubricating oil inflow gap δ has a constant gap dimension in each part in the axial direction. The base end of the annular flange portion 7c continues to the intermediate height position in the nozzle forming protrusions 7b at a plurality of locations in the circumferential direction. In a place where the nozzle forming protrusion 7b is not present, the base end of the annular flange 7c continues to the annular protrusion 7d that protrudes following the entire inner periphery of the annular body 7a.

  At one place in the circumferential direction of the lubricating oil introduction member 7, there is provided an oil discharge port 10 for discharging the lubricating oil supplied to the inside of the rolling bearing 1 to the outside. The oil discharge port 10 is a notch-like portion provided at the end of the annular main body 7a of the lubricating oil introducing member 7, but may be a through hole located in the middle of the annular main body 7a in the width direction.

  In FIG. 2, the discharged lubricating oil regulating member 15 is a member that regulates the scattering of the lubricating oil discharged from the nozzle 8 of the lubricating oil introducing member 7 and released to the outer diameter side, and is open to the rolling bearing 1 side. The ring member has a cross-sectional groove shape. The nozzle forming protrusion 7b of the lubricating oil introduction member 7 is provided at a position biased toward the bearing side in the annular body 7a, and the discharged lubricating oil regulating member 15 is adjacent to the back surface of the nozzle forming protrusion 7b in the annular body 7a. And it is attached to the inner diameter surface of the annular main body 7a in a fitted state.

According to the rolling bearing lubrication device having this configuration, the lubricating oil also serving as a cooling medium introduced from the outer diameter side of the lubricating oil introduction member 7 through the oil supply passage 9 is directed from the nozzle 8 toward the circumferential groove 6 of the inner ring 2. It is ejected and received by the circumferential groove 6 of the inner ring 2.
The lubricating oil received by the circumferential groove 6 is used for cooling the inner ring from the bottom surface of the circumferential groove 6, and a part of the lubricating oil flows into the axial through hole 52 that penetrates the inner ring 2 in the axial direction. It is discharged from the end face of the inner ring at the end and is further used for cooling the inner ring 2 during the passage of the axial through hole 52. The remainder of the lubricating oil received by the circumferential groove 6 is discharged from the circumferential groove 6 to the outer diameter side by centrifugal force. A part of the lubricating oil discharged to the outer diameter side flows into the bearing from the lubricating oil inflow gap δ between the annular flange 7c of the lubricating oil introducing member 7 and the outer diameter inclined surface 2c of the inner ring 2. Used for lubrication. The lubricating oil that has entered the lubricating oil inflow gap δ flows toward the raceway surface 2 c due to the centrifugal force and surface tension generated by the rotation of the inner ring 2. The lubricating oil discharged from the circumferential groove 6 to the outer diameter side of the annular flange portion 7c is discharged from the oil discharge port 10 of the lubricating oil introducing member 7 to the outside as discharged oil. Further, the lubricating oil that has passed through the axial through hole 52 is discharged to the outside from an oil discharge path provided in the bearing box.

The lubricating oil flowing into the axial through hole 52 of the inner ring 2 is used for cooling the inner ring 2 as described above, but cools the inner ring 2 in the entire length direction of the axial through hole 52. Therefore, the inner ring 2 is uniformly cooled in the axial direction, and the difference in the cooling distribution in the axial direction of the inner ring raceway surface 2a can be suppressed. Therefore, unevenness of the surface pressure distribution of the cylindrical roller 4 can be avoided.
Unlike the one provided on the end face of the inner ring 2, the axial through hole 52 is provided with the bottom surface of the circumferential groove 6 on the end face of the inner ring as an inlet, so that the lubricating oil discharged from the nozzle 8 is contained in the circumferential groove 6. It accumulates temporarily and flows into each axial direction through-hole 52 efficiently. Therefore, the lubricating oil discharged from the nozzle 8 contributes efficiently to uniform cooling.

A part of the lubricating oil that has flowed into the axial through hole 52 flows out from the lubricating oil supply hole 54 serving as a branch path to the flanges on both sides of the inner ring 2 and the polishing theft 53 on the end of the raceway surface. For this reason, lubricating oil is supplied to the flange surface that is likely to be insufficiently lubricated due to sliding contact or skew, and the roller end surface is well lubricated. Moreover, lubricating oil is also supplied to the raceway surface, so that insufficient lubrication can be avoided.
Since the lubricating oil supply passages 54 are provided in the polishing thefts 53 on both sides, the lubricating oil can be supplied evenly from the left and right while supplying the lubricating oil from the nozzle 8 on one side. Since the lubricating oil hole 54 is opened in the polishing theft 53, the durability of the cylindrical roller 4 and the raceway surface 2a is reduced due to the formation of the lubricating oil hole 54 compared to the case where the lubricating oil hole is opened in the raceway surface 2a. There is no problem.

  Note that the amount of lubricating oil used for bearing lubrication is preferably the minimum required amount considering the stirring resistance, and if a small amount of lubricating oil after cooling is used is introduced into the bearing. It is enough. Therefore, in this embodiment, the lubricating oil inflow gap δ is set to be appropriately small so that the lubricating oil discharged from the circumferential groove 6 is difficult to enter the bearing. For this reason, only the minimum necessary amount of lubricating oil enters the bearing, and the stirring resistance of the bearing can be reduced, whereby the driving torque of the main shaft 25 can be reduced.

FIG. 4 shows another embodiment of the present invention. In this embodiment, in the first embodiment shown in FIGS. 1 to 3, the lubricating oil supply hole 54 is opened from the bottom surface of the circumferential groove 6 of the inner ring 2 instead of branching from the axial through hole 52. It is. The lubricating oil supply holes 54 are provided, for example, at a plurality of locations in the circumferential direction of the inner ring 2 at equal intervals. Although the lubricating oil supply hole 54 and the axial through hole 52 are shown in the same cross section in the figure, it is preferable that the lubricating oil supply hole 54 and the axial through hole 52 are shifted in the circumferential direction. Also in this case, the lubricating oil supply hole 54 has a smaller diameter than the axial through hole 52. Other configurations in this embodiment are the same as those in the first embodiment.
Thus, even if the lubricating oil supply hole 54 is opened from the circumferential groove 6, the lubricating oil can be supplied to the saddle surface and the raceway surface.

  Although illustration is omitted, when the lubricating oil supply hole 54 is opened from the circumferential groove 6, of the two lubricating oil supply holes 54 in the example of FIG. Only the lubrication hole 54 that opens to the surface polishing stealer 53 may be provided.

  5 and 6 show still another embodiment of the present invention. In this embodiment, instead of providing the annular flange 7c of the lubricating oil introduction member 7 in the first embodiment, the inner diameter surface of the cage 5 is opposed to the outer diameter inclined surface 2c of the inner ring 2, and the lubricating oil inflow gap is provided. It is formed on the outer diameter slope 5c forming δ. Other configurations in this embodiment are the same as those in the first embodiment shown in FIGS.

In the case of this embodiment, the following advantages are obtained. That is, when the rolling bearing 1 is a cylindrical roller bearing, the axial positions of the inner ring 2 and the outer ring 3 may shift due to thermal expansion of the main shaft. When such a positional deviation occurs, if the annular flange 7c for forming the lubricating oil inflow gap δ is provided on the lubricating oil introducing member 7 formed of the outer ring spacer as in the first embodiment, the lubricating oil The size of the inflow gap δ varies.
However, when the outer diameter inclined surface 5c for forming the lubricating oil inflow gap δ is provided in the retainer 5 as in the embodiment of FIG. 5, the retainer 5 is not affected even if the inner ring 2 and the outer ring 3 are displaced in the axial direction. Since it moves in the axial direction integrally with the inner ring 2, the interval of the lubricating oil inflow gap δ is kept constant. Therefore, the amount of lubricating oil flowing into the bearing can always be kept constant regardless of the thermal expansion of the main shaft.

FIG. 7 shows still another embodiment of the present invention. In this embodiment, instead of providing the annular flange 7c of the lubricating oil introducing member 7 in the first embodiment shown in FIGS. 1 to 3, an annular protrusion 22 is provided on the inner ring spacer 21, and this annular protrusion 22 is formed at an inner diameter slope 22ba that forms a lubricating oil inflow gap δ opposite to the outer diameter slope 2c of the inner ring 2.
The annular protrusion 22 includes a standing wall portion 22a that rises from an end portion of the inner ring spacer 21, and a cylindrical portion 22b that extends from the outer diameter side end of the standing wall portion 22a to the inner ring side, and the tip of the cylindrical portion 22b. The inner diameter surface is the inner diameter inclined surface 22ba. The annular protrusion 22 covers the circumferential groove 6 on the end face of the inner ring 2, and lubricating oil passage openings 23 are provided at equal intervals in a plurality of locations in the circumferential direction of the standing wall portion 22a. Other configurations in this embodiment are the same as those in the first embodiment shown in FIGS.

In the case of this embodiment, the lubricating oil discharged from the nozzle 8 passes through the lubricating oil passage opening 23 provided in the annular protrusion 22 of the inner ring spacer 21 and reaches the circumferential groove 6 of the inner ring 2. The lubricating oil received by the circumferential groove 6 of the inner ring 2 is used for cooling the inner ring 2 from the bottom surface of the circumferential groove 6 as in the first embodiment, and a part of the lubricating oil is formed in the axial through hole 52. It flows in and is used for uniform cooling of the inner ring 2, and the rest is discharged to the outer diameter side of the circumferential groove 6 by centrifugal force. Part of the lubricating oil released to the outer diameter side is used for lubrication from the lubricating oil inflow gap δ between the annular protrusion 22 of the inner ring spacer 21 and the outer diameter inclined surface 2c of the inner ring.
In this case, since the inner diameter slope 22ba forming the lubricating oil inflow gap δ is provided in the inner ring spacer 21, the inner ring spacer 21 is integrated with the inner ring 2 even if the axial positions of the inner ring 2 and the outer ring 3 are shifted. , The interval of the lubricating oil inflow gap δ is kept constant. Therefore, also in this embodiment, the amount of lubricating oil flowing into the bearing can always be kept constant regardless of the thermal expansion of the main shaft.

  FIG. 8 shows still another embodiment of the present invention. In this embodiment, in the first embodiment shown in FIGS. 1 to 3, the annular flange portion 7c of the lubricating oil introduction member 7 is simply omitted. In the case of this embodiment, the effect of regulating the amount of lubricating oil due to the lubricating oil inflow gap is not obtained, but part of the lubricating oil released from the circumferential groove 6 of the inner ring 2 to the outer diameter side is the outer diameter of the inner ring 2. It is used for bearing lubrication along the slope 2c. Other configurations and effects in this embodiment are the same as those in the first embodiment.

FIG. 9 shows still another embodiment of the present invention. In this embodiment, in the first embodiment shown in FIGS. 1 to 3, instead of the linear axial through hole 52, the axial through hole 52 is connected to the bottom portion of the circumferential groove 6. Is inclined in the same way as the circumferential groove 6, bent in the middle, and the outlet side portion 52 b is inclined opposite to the inlet side portion 52 a, so that the end face F 2 of the inner ring opposite to the side where the circumferential groove 6 is located It has a shape that penetrates through. Such a shape of the axial through hole 52 is effectively applied when the circumferential groove 6 is inclined with respect to the axial direction so as to be located closer to the radial center as the distance from the inner ring end face F1 increases.
In the case of this embodiment, since the inlet side portion 52 a of the axial through hole 52 has the same inclination as the circumferential groove 6, the lubricating oil in the circumferential groove 6 tends to flow into the axial through hole 52. For this reason, the flow rate of the lubricating oil flowing through the axial through hole 52 is increased, and the inner ring 2 can be effectively cooled. Further, since the outlet side portion 52b of the axial through hole 52 is inclined in the direction opposite to the inlet side portion 52a, a centrifugal force is generated in the outlet side portion 52a due to the rotation of the inner ring, and lubrication occurs from the axial through hole 52. Oil can be discharged efficiently.

  In each of the above embodiments, an example in which a cylindrical roller bearing is used as the rolling bearing 1 has been described. However, the present invention is not limited to this, and the present invention is applicable to lubrication of various types of rolling bearings, for example, angular ball bearings. It is also applicable to.

  FIG. 10 shows an example of a high-speed spindle device provided with the rolling bearing lubrication device according to any one of the embodiments of the present invention. The spindle device 24 is applied to a machine tool, and a tool or workpiece chuck is attached to the front side (machining side) end of the main shaft 25. The main shaft 25 is supported by a plurality of (here, two) rolling bearings 1 separated in the axial direction. Here, the front end of the main shaft 25 is supported by a rolling bearing 1 made of an angular ball bearing, and the rear side of the main shaft 25 is supported by a rolling bearing 1 made of, for example, a cylindrical roller bearing shown in FIG. As with the rolling bearing 1 made of a cylindrical roller bearing, the lubricating device shown in FIG. 1 is also provided for the rolling bearing 1 made of an angular ball bearing. The inner ring 2 of each rolling bearing 1 is fitted to the outer diameter surface of the main shaft 25, and the outer ring 3 is fitted to the inner diameter surface of the bearing housing 26. As for the rolling bearing 1 on the front side of the main shaft, the inner ring 2 is fixed in the bearing box 26 by the stepped surface 25a of the main shaft 25, and the outer ring 3 by the pressing lid 28A through the outer ring positioning spacer 20. As for the rolling bearing 1 on the rear side of the main shaft, the inner ring 2 is fixed in the bearing box 26 by the inner ring positioning spacer 27 and the outer ring 3 is fixed by the pressing lid 28B through the outer ring positioning spacer 20. The bearing box 26 has a double structure of an inner peripheral bearing box 26A and an outer peripheral bearing box 26B, and a cooling groove 29 is formed between the inner and outer bearing boxes 26A, 26B. A lubricating oil introduction member 7 is disposed on the other end face side of the outer ring 3 of the both rolling bearings 1, and an inner peripheral bearing box 26 </ b> A is interposed between the lubricating oil introduction members 7 and 7. An inner ring spacer 30 is interposed between the inner rings 2 and 2 of the both rolling bearings 1. A bearing fixing nut 31 that presses against the inner ring positioning spacer 27 and fixes the rolling bearing 1 is screwed to the rear end portion of the main shaft 25.

  The holding lids 28A and 28B are respectively provided with cooling oil introduction holes 33 for introducing lubricating oil cooled from a cooling oil supply device 32 which is a supply source when the rolling bearing 1 is jet lubricated. These cooling oil introduction holes 33 communicate with a cooling oil supply path 34 provided in the inner peripheral bearing box 26 </ b> A, and the cooling oil supply path 34 communicates with an oil supply path 9 of the lubricating oil introduction member 7. The oil supply path from the cooling oil supply device 32 includes a first oil supply path 38 communicating with the cooling groove 29 in the bearing box 26 from the cooling oil introduction hole 43 of the outer peripheral bearing box 26B, an oil filter 40, and a pressure regulating valve 41. Then, it branches off to the second oil supply passage 39 communicating with the cooling oil introduction hole 33 of the presser lids 28A, 28B. The drain oil supplied to the cooling groove 29 in the bearing box 26 and used for cooling the bearing box 26 is collected from the drain oil outlet hole 44 of the outer peripheral bearing box 26B to the cooling oil supply device 32. In addition, oil pressure holes 35 are provided in the presser lids 28A and 28B, and these oil pressure holes 35 communicate with the oil discharge port 10 of the lubricating oil introducing member 7 from the oil discharge path 36 provided in the inner peripheral bearing box 26A. The drain oil used for cooling the bearing is recovered by the cooling oil supply device 32 via the oil drain port 10 → the oil drain passage 36 → the oil drain hole 35 → the oil drain pump 37.

In the spindle device 24 configured as described above, since the rolling bearing lubrication device described above is incorporated, the agitation resistance due to oil supply into the rolling bearing 1 is small, the driving torque of the main shaft 25 can be reduced, the speed is increased, and the temperature is increased. Reduction is possible.
In addition, although this spindle apparatus 24 demonstrated the case where the lubrication apparatus of the rolling bearing which concerns on 1st Embodiment was applied, you may use the lubrication apparatus of the rolling bearing which concerns on any other embodiment.

It is sectional drawing of the lubricating device of the rolling bearing which concerns on 1st Embodiment of this invention. It is a partial expanded sectional view of the lubricating device. (A) is a front view of a lubricating oil introducing member in the rolling bearing lubrication device of the same embodiment, and (B) is a IIIB-O-IIIB ′ sectional view thereof. It is a partial expanded sectional view of the lubricating device of the rolling bearing which concerns on other embodiment of this invention. It is a partial expanded sectional view of the lubricating device of the rolling bearing which concerns on further another embodiment of this invention. (A) is the elements on larger scale of the lubricating oil introducing | transducing member in the lubricating device of the rolling bearing of the embodiment, (B) is the front view. (A) is a partial expanded sectional view of the lubricating device of the rolling bearing which concerns on further another embodiment of this invention, (B) is the partial front view of the inner ring | wheel spacer. It is a partial expanded sectional view of the lubricating device of the rolling bearing which concerns on further another embodiment of this invention. It is a partial expanded sectional view of the lubricating device of the rolling bearing which concerns on further another embodiment of this invention. It is a block diagram of the spindle apparatus provided with the lubricating device of the rolling bearing of this invention. It is a fragmentary sectional view which shows the lubricating device of the rolling bearing which concerns on a proposal example.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Rolling bearing 2 ... Inner ring 2c ... Outer diameter slope 3 ... Outer ring 4 ... Cylindrical roller (rolling element)
DESCRIPTION OF SYMBOLS 5 ... Retainer 5c ... Inner diameter slope 6 ... Circumferential groove 7 ... Lubricating oil introduction member 7c ... Annular flange 8 ... Nozzle 21 ... Inner ring spacer 22ba ... Inner diameter slope 52 ... Axial through-hole 52a ... Inlet side part 52b ... Outlet Side portion 53 ... Polishing stealing 54 ... Lubricating oil supply holes F1, F2 ... Inner ring end face δ ... Lubrication oil introduction gap

Claims (6)

  A circumferential groove is provided on the end face of the inner ring of the rolling bearing, and a nozzle for discharging lubricating oil that also serves as a bearing cooling medium is provided in the circumferential groove on the lubricating oil introduction member adjacent to the outer ring of the rolling bearing, A rolling bearing lubrication device comprising axial through holes at a plurality of locations in a circumferential direction through which an inner ring penetrates in an axial direction from the bottom surface of the circumferential groove and allows the lubricating oil in the circumferential groove to pass therethrough.   In Claim 1, the rolling bearing is a cylindrical roller bearing with an inner ring rod, and the lubricating oil supply holes respectively connected to the polishing theft formed at corners between the flange surface and the raceway surface on both sides of the inner ring, A rolling bearing lubrication device provided by branching from an axial through hole.   In Claim 1, the rolling bearing is a cylindrical roller bearing with an inner ring flange, and a lubricating oil supply hole leading to a polishing steal formed at a corner between the flange surface and the raceway surface of the inner ring is provided from the circumferential groove. Lubricating device for rolling bearings provided.   The rolling bearing lubrication device according to claim 2 or 3, wherein an inner diameter of the lubricating oil supply hole is smaller than an inner diameter of the axial through hole.   5. The axial groove according to claim 1, wherein the circumferential groove is inclined with respect to the axial direction so as to be positioned closer to the radial center as the distance from the end face of the inner ring increases. The end surface of the inner ring on the opposite side has an inlet side portion connected to the bottom of the circumferential groove having the same inclination as the circumferential groove, bent in the middle, and the outlet side portion inclined in the direction opposite to the inlet side portion. Lubricating device for rolling bearings.   The rolling bearing lubrication device according to any one of claims 1 to 5, wherein the rolling bearing is used as a main shaft bearing of a machine tool.

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