JP4836852B2 - Angular contact ball bearing lubrication system - Google Patents

Description

  The present invention relates to a lubricating device for an angular ball bearing used for supporting a high-speed spindle such as a spindle for a machine tool.

  Machine tool spindles are becoming increasingly faster in order to increase machining efficiency. As the spindle speed increases, torque and heat generation increase in the spindle bearing. In order to cope with this, jet lubrication that simultaneously lubricates and cools the bearing by injecting a large amount of oil into the bearing is used. However, this jet lubrication generally has a drawback that the power loss is increased due to the agitation resistance caused by the oil contained in the bearing.

  Therefore, a new jet lubrication structure has been proposed in which the amount of lubricating oil entering the bearing is limited to reduce the agitation resistance due to oil (for example, Patent Document 1). The new jet lubrication structure disclosed in Patent Document 1 cools the inner ring heat generation by receiving the lubricant discharged from the lubricant introduction member composed of an outer ring side spacer or the like by a circumferential groove provided on the end face of the inner ring. is there. Most of the cooled lubricating oil is discharged out of the bearing, but a part of it is used for bearing lubrication, and the gap between the lubricating oil introduction member and the outer ring slope of the inner ring is used for the inner ring raceway surface. Inflow. That is, only a small amount of lubricating oil required for bearing lubrication enters the bearing. For this reason, stirring resistance becomes small and the power loss of a bearing also becomes small.

Conventionally, in order to lubricate and cool the bearing, a lubrication method called under-lace lubrication in which axial through holes are provided at a plurality of locations in the circumferential direction of the inner ring and a part of the lubricating oil is circulated through the through holes. Has been done. Furthermore, in this under-lace lubrication, in order to ensure the supply of lubricating oil into the bearing and through hole, a nozzle that discharges lubricating oil into the bearing and a nozzle that discharges lubricating oil toward the through hole Have been proposed (for example, Patent Document 2).
JP 2006-118525 A Utility model registration No. 2503488

  The new jet lubrication structure disclosed in Patent Document 1 and the like can suppress the power loss of the bearing by limiting the amount of lubricating oil entering the bearing, but has the following problems. In other words, since the lubricating oil is accumulated in a circumferential groove provided on one end face of the inner ring to cool the inner ring, it is difficult to efficiently cool the entire inner ring, and the axial direction is unevenly cooled. . If the inner ring is not sufficiently cooled or the inner ring is not evenly cooled in the axial direction, an excessive preload due to the temperature difference between the inner and outer rings occurs. In a bearing used for a spindle of a machine tool or the like, an increase in the preload amount or an excessive increase in the inner ring temperature is not preferable because it leads to seizure or poor rotation accuracy.

  Conventional underlace lubrication has problems in supplying lubricating oil and cooling the outer ring. Further, the method using both the under-lace lubrication and the jet lubrication disclosed in Patent Document 2 has a problem that a large amount of power is required to supply the lubricant because the lubricant is discharged from the two nozzles.

  An object of the present invention is to provide lubrication of an angular ball bearing that can supply lubricating oil that also serves as cooling of the bearing, thereby efficiently cooling the inner ring in the axial direction and that does not require much power to supply the lubricating oil. Is to provide a device.

Lubrication system for the inventions of the angular ball bearing, a circumferential groove is provided on the end face of the inner ring of the angular contact ball bearing, this circumferential groove, a nozzle for discharging the lubricating oil also serves as a bearing cooling medium, wherein the angular contact ball bearings Provided in a lubricating oil introduction member adjacent to the outer ring, and through holes are provided at a plurality of locations 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. It is characterized by that.

According to this configuration, the lubricating oil discharged from the nozzle is received in a circumferential groove formed in the end face of the inner ring, to cool the inner ring from the end face. Part of the lubricating oil received in the circumferential groove is discharged from the circumferential groove to the outer diameter side by centrifugal force, and a part of the lubricating oil flows into the bearing. Thereby, the raceway surface of the bearing is lubricated. Some of the remaining lubricating oil received in the circumferential groove passes through the through holes provided in the circumferential direction of the plurality of positions of the inner ring, to cool the inner ring in the entire length direction of the through hole . Therefore, the inner wheel is efficiently cooled, moreover its cooling is performed uniformly in the axial direction. The through hole, since the bottom surface of the circumferential groove formed in the end surface of the inner wheel becomes an inlet, lubricating oil discharged from the nozzle flows efficiently through holes accumulated temporarily in the circumferential groove . Therefore, the lubricating oil discharged from the nozzle, effectively contributes to the cooling of the inner wheel. As described above, since the lubricating oil in the circumferential groove is distributed and supplied to the inside of the bearing and the through hole, only one nozzle for discharging the lubricating oil is required, and the power required for supplying the lubricating oil can be reduced. .

Before SL circumferential groove, it is inclined to the axial direction so as to be located more radially inboard the distance from the end face of the inner ring. The pre SL through hole, the inlet side communicating with the bottom of the circumferential groove and the same inclination and said circumferential groove, is bent in the middle, the opposite side is an outlet side and the inclination of the inlet side and the opposite It shall be the one of the was allowed to penetrate missing on the end face of the inner ring.
When the inclination of the inlet side portion of the through hole is the same as the inclination of the circumferential groove, the lubricating oil in the circumferential groove tends to flow into the through hole. For this reason, the flow rate of the lubricating oil flowing through the through hole is increased, and the inner ring can be effectively cooled. Further, the through hole is bent halfway, and the outlet side portion is inclined in the direction opposite to the inlet side portion and penetrates the end surface of the opposite inner ring, so that the inner ring is connected to the outlet side portion of the through hole. Centrifugal force is generated by rotation. For this reason, lubricating oil can be efficiently discharged | emitted from a through-hole.
Further, by bending the through hole as described above, the shortest distance from the inner ring raceway surface to the through hole can be increased, and the proof stress against the load from the rolling element is increased.

Further, in the present invention, a portion of the outer diameter surface and the lubricating oil introducing member of the annulus is opposed via a predetermined gap, this gap, a portion of the lubricating oil discharged from the nozzle front wheels A lubricating oil introduction path that leads to the raceway surface may be used.
Thus, the gap between the portion of the outer diameter surface and the lubricating oil introducing member of the inner wheel when the lubricating oil introducing passage, only the minimum amount necessary for lubricating the bearings of the lubricating oil discharged from the nozzle Can be guided into the bearing. Therefore, while performing lubrication that can cope with high-speed rotation of the main shaft, it is possible to reduce the agitation resistance due to the oil that has entered the bearing and to reduce the power loss of the bearing.

  In this invention, the angular ball 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 angular ball bearing lubrication device according to the present invention, a circumferential groove is provided on the end face of the inner ring of the angular ball bearing, and a nozzle that discharges lubricating oil that also serves as a bearing cooling medium is provided in the circumferential groove of the angular ball bearing. provided the lubricating oil introducing member adjacent to the outer ring, the through hole from the bottom surface of the circumferential groove through the inner ring in the axial direction to pass the lubricating oil of the circumferential groove, set in a plurality of positions in the circumferential direction The circumferential groove is inclined with respect to the axial direction so that it is located closer to the center in the radial direction as it is farther from the end face of the inner ring, and the through-hole has an inlet side portion connected to the bottom of the circumferential groove. the same slope as the circumferential grooves, is bent in the middle, because the are those that gave penetrate omission on the end face of the inner ring on the opposite side becomes the outlet side and the inclination of the inlet side and the opposite, the cooling of the bearing Lubricating oil can also be supplied so that the inner ring can be efficiently and shafted. Can uniformly cool countercurrent, yet was the one that does not require too large power to the lubricating oil supply.

A first reference proposal example of the present invention will be described with reference to FIGS. FIG. 1 shows a cross-sectional view of the angular ball bearing lubricating device of this reference proposal example . This angular ball bearing lubrication device jets a large amount of lubricating oil from the lubricating oil introducing member 7 toward the angular ball bearing 1 to simultaneously lubricate and cool the bearing. The angular ball bearing 1 is used as a main shaft bearing of a machine tool, and as shown in an enlarged view in FIG. 2, between the inner ring 2, the outer ring 3, and the raceway surfaces 2a and 3a of these inner and outer rings 2 and 3. And a plurality of rolling elements 4 interposed therebetween. The rolling element 4 is formed of a ball, and is held by a ring-shaped cage 5 at a predetermined interval in the circumferential direction. The inner ring 2 is fitted to the outer diameter surface of the main shaft 25. The outer ring 3 is fixed in a bearing box (not shown).

  A circumferential groove 6 is provided on the end face F1 of the inner ring 2 on the side opposite to the load (bearing rear side). The circumferential groove 6 is formed from the end face F1 of the inner ring 2 to the outer diameter surface. The circumferential groove 6 is inclined with respect to the axial direction so as to be located closer to the center in the radial direction as it is farther from the end face F1. The portion on the outer diameter side of the inner ring 2 opposite to the raceway surface 2a is an outer-diameter slope 2b that increases in diameter as it approaches the raceway surface 2a side from the end face F1. The end face F1 side having the circumferential groove 6 of the inner ring 2 is positioned by the inner ring spacer 21.

  The inner ring 2 is provided with through holes 52 that penetrate 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 through at a plurality of positions in the circumferential direction at equal intervals. ing. In this embodiment, the through hole 52 is a straight hole facing in the axial direction. The outlet of the through hole 52 opens into the oil drain groove 14 provided in the inner ring positioning member 27 described later.

The lubricant introduction member 7 is an outer ring positioning spacer that is disposed adjacent to the outer ring 3 on the end face F1 side where the circumferential groove 6 of the inner ring 2 of the angular ball bearing 1 is provided, and is fixed in the bearing box. The The lubricant introduction member 7 is combined with a release lubricant regulation member 15.
The lubricating oil introduction member 7 includes a nozzle 8 that discharges the lubricating oil into the circumferential groove 6 of the inner ring 2 of the angular ball bearing 1, and extends from the outer diameter surface of the lubricating oil introduction member 7 toward the inner diameter side. A communicating oil passage 9 is formed. In this embodiment, the nozzle 8 is provided at an inclination angle that matches the inclination of the circumferential groove 6.

  As shown in FIG. 3, the lubricating oil introduction member 7 is provided with nozzle forming protrusions 7b protruding toward the inner diameter side at a plurality of equally spaced positions (for example, three positions) in the circumferential direction of the annular body 7a. The nozzle 8 is provided on each nozzle forming 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.

  An annular flange 7 c that protrudes into the bearing space of the rolling bearing 1 is provided at the end of the lubricating oil introducing member 7 on the rolling bearing 1 side. The annular flange 7c is formed with an inner diameter slope 7ca having an inner diameter surface at the tip thereof facing the outer diameter slope 2b of the inner ring 2 via a gap δ. The inner diameter slope 7ca is parallel to the outer diameter slope 2b of the inner ring 2, and the gap δ has a constant gap dimension in each part in the axial direction. The gap δ is a lubricating oil introduction path that guides a part of the lubricating oil discharged from the nozzle 8 to the raceway surface 2a of the front wheel 2.

  In one place of the end face of the lubricating oil introducing member 7 on the side where the discharged lubricating oil regulating member 15 is combined, the lubricating oil discharged from the nozzle 8 into the circumferential groove 6 does not enter the bearing space. A bearing outer oil discharge port 10 for discharging to the outside is provided. In addition, on the end surface of the lubricating oil introducing member 7 opposite to the side where the outer bearing oil draining port 10 is provided, the lubricating oil supplied to the inside of the rolling bearing 1 is discharged to the outside. A groove 11 and a bearing oil drain port 12 are provided. The in-bearing oil drain groove 11 is an annular groove, and the in-bearing oil drain port 12 is opened at one location of the in-bearing oil drain groove 11. The bearing outer oil outlet 10 and the bearing inner oil outlet 12 are provided at the same position in the circumferential direction. The bearing outer oil outlet 10 and the bearing inner oil outlet 12 are notched portions provided at the end of the annular main body 7a of the lubricating oil introducing member 7, but in the middle of the annular main body 7a in the width direction. It is good also as a through-hole located.

  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. The discharged lubricating oil regulating member 15 is a ring member having a groove shape in cross section opened to the rolling bearing 1 as a whole, but a part of the outer diameter portion is notched at the circumferential position of the bearing outer oil discharge port 10. Thus, the oil passage port 15a is connected, and the space on the circumferential groove 6 side of the lubricating oil introduction member 7 and the bearing outer oil discharge port 10 communicate with each other through the oil passage port 15a (FIG. 1). .

According to the lubrication device for the angular ball bearing having this configuration, the lubricating oil also serving as a cooling medium introduced from the outer diameter side of the lubricating oil introducing member 7 through the oil supply passage 9 is directed from the nozzle 8 toward the circumferential groove 6 of the inner ring 2. And is 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 through-hole 52 penetrating the inner ring 2 in the axial direction and enters the other end. It is discharged from the inner ring end face F2 and further used for cooling the inner ring 2 during the passage of the 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 2b 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 a due to the centrifugal force and surface tension generated by the rotation of the inner ring 2. The lubricating oil that has passed through the through hole 52 is discharged from the oil drain groove 14 to the outside through a drain oil path provided in the bearing housing. Further, the lubricating oil that has not flowed into either the through hole 52 or the lubricating oil inflow gap δ is discharged to the outside from the bearing outer oil outlet 10 of the lubricating oil introduction member 7 as discharged oil.

The lubricating oil that has flowed into the 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 through hole 52. Therefore, the inner ring 2 can be efficiently cooled. Moreover, cooling is performed uniformly in the axial direction.
In the through hole 52, the bottom surface of the circumferential groove 6 provided in the inner ring end face F1 serves as an inlet, so that the lubricating oil discharged from the nozzle 8 temporarily accumulates in the circumferential groove 6 and efficiently passes through each through hole. 52. Therefore, the lubricating oil discharged from the nozzle 8 contributes efficiently to the cooling of the inner ring 2.

  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. Therefore, only the minimum necessary amount of lubricating oil enters the bearing, and the stirring resistance of the bearing can be reduced, thereby reducing the power loss of the bearing 1.

Figure 4 relates to an embodiment of the present invention, showing a modified example above first reference proposed example. In this modified example, in the first reference proposal example , instead of the linear through hole 52, the through hole 52 has the same inclination as the circumferential groove 6 in the inlet side portion 52 a connected to the bottom of the circumferential groove 6. The outlet side portion 52b is inclined in the opposite direction to the inlet side portion 52a so as to penetrate through the inner ring end face F2 opposite to the side where the circumferential groove 6 is provided. Such a shape of the 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. Other configurations in this modification are the same as those in the first reference proposal example .
In the case of this modification, the inlet side portion 52 a of the through hole 52 has the same inclination as that of the circumferential groove 6, so that the lubricating oil in the circumferential groove 6 tends to flow into the through hole 52. For this reason, the flow rate of the lubricating oil flowing through the through hole 52 is increased, and the inner ring 2 can be effectively cooled. Further, since the outlet side portion 52b of the 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 the lubricating oil is efficiently supplied from the through hole 52. Can be discharged.
Furthermore, by bending the through hole 52 as described above, the shortest distance from the inner ring raceway surface 2a to the through hole 52 can be increased, and the proof stress against the load from the rolling element 4 is increased.

FIG. 5 shows a second reference proposal example of the present invention. This second reference proposal example differs from the first reference proposal example shown in FIGS. 1 to 3 in the following points. That is, in the second reference proposal example , the inner ring spacer has a first inner ring spacer 21A adjacent to the inner ring 2 and a second inner ring spacer in contact with the end surface of the first inner ring spacer 21A opposite to the inner ring 2. It is divided into 21B. In the first reference proposal example , the inner circumferential groove 6 is provided in the end face F1 of the inner ring 2, whereas in the second reference proposal example , the first inner ring spacer 21A is opposite to the inner ring 2 side. An inner circumferential groove 6 is provided on the end face F3. The circumferential groove 6 of the second reference proposal example is formed from the upper part of the end face F3 of the inner ring 2 to the outer diameter surface. The diameter of the inner ring side end of the second inner ring spacer 21B is larger than the diameter of the end opposite to the inner ring 2 of the first inner ring spacer 21A, and the inner ring side end face F4 of the second inner ring spacer 21B The surface of the groove 6 on the side opposite to the inner ring 2 is closed, and the circumferential groove 6 is open only on the surface on the outer diameter side.
The first inner ring spacer 21A and the inner ring 2 have through holes 52 that pass through the first inner ring spacer 21A and 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. Are provided at a plurality of locations in the circumferential direction at equal intervals. In this embodiment, the through hole 52 is a straight hole facing in the axial direction.

The outer diameter surface of the first inner ring spacer 21 </ b> A is formed as a slope 21 </ b> Aa following the outer diameter slope 2 b of the inner ring 2. The inner diameter slope 7da of the covered portion 7d of the lubricating oil introducing member 7 is opposed to the outer diameter slope 21Aa of the first inner ring spacer 21A via a gap δ. The covering portion 7d is a donut disk-like portion integrated at the base end with the nozzle forming protrusion 7b, and is provided instead of the annular flange portion 7c in the first embodiment. The inner diameter slope 7da of the covered portion 7d is parallel to the outer diameter slope 2b of the inner ring 2, and the gap δ has a constant gap dimension in each part in the axial direction. This gap δ is a lubricating oil introduction path that guides part of the lubricating oil discharged from the nozzle 8 to the raceway surface 2 a of the front wheel 2.
Other configuration in the second reference proposal example is the same as the first reference proposed example shown in FIGS.

In the case of the second reference proposal example , the same operation and effect as the first reference proposal example can be obtained. In addition, since the circumferential groove 6 is provided in the inner ring spacer 21 in the second reference proposal example , there is an advantage that it is not necessary to process the circumferential groove 6 in the inner ring 2. Since the bearing ring of the bearing requires high-precision machining and advanced heat treatment, machining the circumferential groove 6 having a complicated shape in the inner ring 2 causes various problems. In this regard, if the circumferential groove 6 is provided in the inner ring spacer 21A, the occurrence of such a problem can be eliminated. Since the inner ring spacers 21A and 21B do not require heat treatment, it is easy to provide the circumferential groove 6 in the first inner ring spacer 21A.

FIG. 6 shows a modification of the second reference proposal example . This modified example is similar to the modified example (FIG. 4) for the first reference proposal example (FIGS. 1 to 3), but instead of the straight through hole 52 in the second reference proposal example , Is bent on the way. Other configurations in this modification are the same as those in the second reference proposal example . The effect of this modification is the same as that of the modification (FIG. 4).

FIG. 7 shows an example of a high-speed spindle device provided with the angular ball bearing lubrication device of the first reference proposal example shown in FIGS. The spindle device 24 is applied to a machine tool, and a tool or workpiece chuck is attached to an end of a main shaft 25. The main shaft 25 is supported by a pair of angular ball bearings 1 at the front (working side) end and the rear end in the axial direction. The spindle housing includes an outer housing 43, an inner housing 44, and a front bearing box 26A and a rear bearing box 26B that are fitted inside the inner housing 44. A motor 45 is accommodated at an axial position between the front bearing box 26A and the rear bearing box 26B.
The inner ring 2 of each angular ball 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 front bearing box 26A or the rear bearing box 26B. The pair of angular ball bearings 1 are provided in a back surface combination, and the inner rings 2 are positioned with respect to each other by an inner ring spacer 21, and the outer rings 3 are positioned with respect to each other by a lubricating oil introduction member 7. A pair of angular contact balls is formed by pressing the inner ring retainer 28 against the inner ring 2 of the angular ball bearing 1 on the shaft end side via the inner ring positioning member 27 and pressing the outer ring retainer 30 against the outer ring 3 via the outer ring positioning member 29. The bearing 1 is fixed to the bearing housings 26A and 26B.

  The bearing housings 26 </ b> A and 26 </ b> B and the outer ring retainer 30 are provided with cooling oil introduction holes 33 for introducing lubricating oil cooled from a cooling oil supply device 32 that is a supply source when the angular ball bearing 1 is jet lubricated. . The cooling oil introduction hole 33 communicates with the oil supply passage 9 of the lubricating oil introduction member 7. The oil supply path 38 from the cooling oil supply device 32 is connected to the cooling oil introduction hole 33 through the oil filter 40 and the pressure adjustment valve 41. The bearing housings 26 </ b> A and 26 </ b> B and the outer ring retainer 30 are provided with oil drain holes 35 that return the oil drained after jet lubrication to the cooling oil supply device 32. The oil drain hole 35 communicates with the oil draining port 10 outside the bearing, the oil draining port 12 outside the bearing, and the oil draining groove 14 of the inner ring positioning member 27. The oil used for cooling and lubrication of the angular ball bearing 1 and flowing out from the oil discharge ports 10 and 12 and the oil discharge groove 14 is recovered from the oil discharge hole 35 through the oil discharge pump 37 to the cooling oil supply device 32. .

Incidentally, the spindle device 24 has been explained a case of applying the lubricating device of the angular contact ball bearing according to the first reference proposed example, lubrication of the angular ball bearing according to any other embodiment shaped state or references propose Example An apparatus may be used.

It is sectional drawing of the lubricating device of the angular ball bearing which concerns on the 1st reference proposal example of this invention. It is a partial expanded sectional view of the lubricating device. (A) is the front view of the lubricating oil introduction member in the lubricating device of the angular ball bearing of the embodiment, (B) is the sectional view. It is parts partial enlarged sectional view of a lubricating apparatus for angular contact ball bearing according to the implementation embodiments of the present invention. It is a partial expanded sectional view of the lubricating device of the angular ball bearing which concerns on the 2nd reference proposal example of this invention. It is a partial expanded sectional view of the modification of the lubricating device of the angular ball bearing which concerns on the 2nd reference proposal example of this invention. It is a block diagram of the spindle apparatus provided with the lubricating device of the angular ball bearing of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Angular contact ball bearing 2 ... Inner ring 2a ... Raceway surface 2b ... Outer diameter slope 3 ... Outer ring 4 ... Rolling element 5 ... Cage 6 ... Circumferential groove 7 ... Lubricating oil introduction member 7c ... Annular collar part 7d ... Cover part 8 ... Nozzle 21 ... Inner ring spacer 21A ... First inner ring spacer 21B ... Second inner ring spacer 21Aa ... Outer diameter slope 52 ... Through hole 52a ... Inlet side part 52b ... Outlet side part F1, F2 ... Inner ring end face δ ... Clearance (lubrication) Oil introduction path)

Claims (3)

A circumferential groove is provided on the end face of the inner ring of the angular ball bearing, and a nozzle that discharges lubricating oil that also serves as a bearing cooling medium is provided in the circumferential groove in the lubricating oil introduction member adjacent to the outer ring of the angular ball bearing, a through hole for passing the lubricating oil of the circumferential groove from the bottom of the circumferential groove through the inner ring in the axial direction, only set to a plurality of positions in the circumferential direction, the circumferential groove, the inner ring of the end face The through hole is inclined with respect to the axial direction so as to be located closer to the center in the radial direction, and the through-hole is bent in the middle with the inlet side portion connected to the bottom of the circumferential groove having the same inclination as the circumferential groove. is allowed, the lubricating device of the angular contact ball bearing, wherein the this is that let penetrate omission on the end face of the inner ring on the opposite side becomes the outlet side and the inclination of the inlet side and opposite.   2. The outer diameter surface of the inner ring and a part of the lubricating oil introduction member are opposed to each other through a predetermined gap, and a part of the lubricating oil discharged from the nozzle is allowed to pass through the gap. Lubricating device for angular contact ball bearings as a lubricating oil introduction path leading to 3. The angular ball bearing lubrication device according to claim 1 , wherein the angular ball bearing is used as a spindle device of a machine tool.

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