JP2006118525A - Lubrication device of rolling bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a lubrication device of a rolling bearing enabling a high-speed operation without increasing a power loss irrespective of the size of the bearing, capable of efficiently guiding a lubricating oil to a raceway surface, and capable of cooling the bearing without a complicated oil supply mechanism. <P>SOLUTION: This lubrication device of the rolling bearing lubricates the rolling bearing by discharging the lubrication oil from a lubrication oil lead-in member 7 into the rolling bearing 1. The lubrication oil lead-in member 7 comprises a discharge port 8 opening to the lateral face of an inner ring 2. A sloped part 2b larger in diameter on the raceway surface 2a side of the inner ring 2 and leading the lubrication oil discharged from the discharge port 8 to the raceway surface 2a of the inner ring 2 by a centrifugal force and a surface tension acting on the lubrication oil is formed on the outer diameter surface of the inner ring 2. A flanged part 10 covering over the sloped part 2b through a clearance δ and guiding the lubrication oil flowing to the raceway surface 2a through the clearance δ is formed on the lubrication oil lead-in member 7. The flanged part 10 is formed to extend to the inner diameter side of a cage 5 holding rolling elements 4, and the inner diameter surface 5a of the cage 5 on the flanged part 10 side is formed in a tapered surface having a larger diameter at the lateral center side. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a lubricating device applied to a rolling bearing for a machine tool main shaft.

  Machine tool spindles tend to increase in speed 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 and air-oil lubrication are often used for lubrication of the main shaft bearing.

  Jet lubrication involves injecting a large amount of oil into the bearing to simultaneously lubricate the bearing and cool the bearing, but this lubrication method increases the agitation resistance of the lubricant when the bearing is operated at high speed ( This is disadvantageous in that the power loss of the bearing increases and a large capacity drive motor is required.

  Air oil lubrication mixes lubricating oil with the carrier air and injects the oil into the bearing from the nozzle. As a measure to reduce the stirring resistance of the oil in the bearing, a small amount of oil is attached to the outer surface of the inner ring. In addition, there has been proposed a system in which oil is supplied to a track portion using centrifugal force and surface tension (for example, Patent Documents 1 and 2).

  For example, in the lubricating structure disclosed in Patent Document 1, as shown in FIG. 5, a scoop portion 50 that is an oil collecting portion is formed on one width surface of the bearing inner ring 42, and an outer ring spacer disposed adjacent thereto. 47, an oil supply nozzle 51 for injecting lubricating oil toward the scoop portion 50 is formed. Further, the scoop portion 50 communicates with the raceway surface of the inner ring 42 through the nozzle hole 52, and most of the lubricating oil supplied from the oil supply nozzle 51 enters the scoop portion 50 and the nozzle hole 52 by centrifugal force. After that, the ball 44 is sprayed.

As shown in FIG. 6 showing the V portion of FIG. 5 in an enlarged manner, there is a gap between the end surface on the formation side of the oil supply nozzle 51 of the outer ring spacer 47 and the end surface on the formation side of the scoop portion 50 of the inner ring 42. A gap C having an amount of 0.2 mm or less is formed, and a part of the lubricating oil supplied from the oil supply nozzle 51 that does not enter the scoop portion 50 and adheres to the end face of the outer ring spacer 47 Passes through the gap C and moves to the end face of the inner ring 42. Further, the outer diameter surface 50a on the formation side of the scoop portion 50 of the inner ring 42 is a tapered surface that expands toward the inner side of the bearing, and the intersection between the inner ring end surface and the outer diameter surface 50a is a curved surface portion 50c. Therefore, the lubricating oil that has moved to the end surface of the inner ring 42 is moved from the curved surface portion 50c to the inner ring outer diameter surface 50a by the centrifugal force accompanying the rotation of the inner ring 42, and is supplied below the cage 45.
Note that the above-mentioned Patent Document 1 also discloses a lubricating structure shown in FIGS. 5 and 6 in which the nozzle hole 52 of the inner ring 42 is omitted (FIG. 7).

Incidentally, air oil used for air oil lubrication has almost no bearing cooling effect. Therefore, when air-oil lubrication is employed, it is necessary to provide a cooling mechanism separately. As such a cooling mechanism, one that cools the housing and cools the bearing by passing cooling oil through the inner diameter portion of the shaft is known (Patent Documents 3 to 5).
JP 2001-012481 A JP 2002-54643 A Japanese Patent No. 3084356 Japanese Patent Laid-Open No. 7-24687 JP-A-7-145819

The lubrication structure disclosed in Patent Document 1 (FIGS. 5 to 7) has a problem that the gap C cannot be set when the bearing size is small or the bearing inner ring 42 is thin. Further, it is necessary to adjust the amount of oil supplied into the bearing with the supply device on the oil supply nozzle 51 side.
Further, the cooling mechanisms of Patent Documents 3 to 5 have a problem that a dedicated rotary joint portion for supplying oil to the inner diameter side of the shaft is necessary, and the structure of the rotary joint portion becomes complicated.

  In order to solve such a problem, the present inventor tried the one shown in FIG. This lubricating device discharges lubricating oil from the discharge port 8 of the lubricating oil introducing member 7 to the circumferential groove 6 on the width surface of the inner ring 2, and the lubricating oil is subjected to the outer diameter surface of the inner ring 2 by centrifugal force and surface tension. Is led to the raceway surface 2a of the inner ring 2 along the inclined surface 2b. In addition, a hook-like portion 10 is provided on the inclined surface portion 2b via a gap δ so that the lubricating oil flowing from the gap δ to the raceway surface 2a is guided.

  However, in the configuration of FIG. 8, as indicated by the arrows, the lubricating oil that has flowed from the circumferential groove 6 to the inclined surface portion 2 b is partially (arrow p), It was found that the tip was blown to the outer diameter side by centrifugal force and did not reach the track surface 2a. For this reason, the lubricating oil discharged from the lubricating oil introducing member 7 is discharged without being lubricated or cooled, resulting in wasted lubricating oil supply.

  The object of the present invention is to enable high speed operation without increasing power loss regardless of the bearing size, to efficiently guide the lubricating oil to the raceway surface, and to cool the bearing without having a complicated oiling mechanism. A lubrication device for a rolling bearing is provided.

  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 for lubrication, and the lubricating oil introduction member opens facing the width surface of the inner ring. The inner ring raceway has a discharge port, the outer ring surface of the inner ring has a larger diameter on the raceway side of the inner ring, and the lubricating oil discharged from the discharge port is subjected to centrifugal force and surface tension acting on the lubricating oil. A slope portion that leads to the surface is provided, and a flange-like portion that covers the slope portion through a gap and guides the lubricant flowing from the gap to the raceway surface is provided on the lubricant introduction member, and the flange-like portion is a rolling element. The cage is extended to the inner diameter side of the cage, and the inner diameter surface of the cage on the side of the flange-shaped portion is a tapered surface having a large diameter at the center in the width direction.

  According to this configuration, the lubricating oil discharged from the discharge port of the lubricating oil introduction member to the inner ring width surface is covered with the inclined surface of the inner ring and the inclined surface by centrifugal force and surface tension acting from the rotation of the inner ring. Guided in the gap between the ridges and supplied to the raceway surface. The lubricating oil flowing in the gap may flow in a state of being pressed against the inner diameter surface side of the bowl-shaped portion by the action of centrifugal force under various conditions such as the rotation speed and the inclination angle. The lubricating oil that flows in this state falls off to the outer diameter side by a centrifugal force at a position where it exits the tip of the bowl-shaped portion. However, the hook-shaped portion extends to the inner diameter side of the cage that holds the rolling elements, and the inner diameter surface of the cage is a tapered surface having a large diameter at the center in the width direction. The lubricating oil that has fallen off to the outer diameter side is received by the tapered surface of the cage and supplied to the rolling elements. For this reason, the lubricating oil supplied to the gap between the slope portion of the inner ring and the hook-like portion is used for lubrication without waste.

Thus, since the lubricating oil discharged from the lubricating oil introduction member is supplied to the raceway surface from the gap between the inner ring slope portion and the flanged portion of the lubricating oil introduction member, a large power loss does not occur, High speed operation is possible without increasing power loss. Since the lubricant is guided between the slope of the outer diameter surface of the inner ring and the hook-shaped part covering it, unlike the case of guiding with a minute clearance on the end face of the inner ring, The present invention can be applied even when the inner ring is thin. Further, since the hook-shaped portion extends to the inner diameter side of the cage and the inner diameter surface of the cage is a tapered surface, the lubricating oil can be efficiently guided to the raceway surface as described above without waste.
In addition, of the lubricant discharged from the discharge port of the lubricant introduction member, the remaining lubricant excluding the inflow flowing into the gap between the slope portion of the inner ring and the flange portion of the lubricant introduction member is used for cooling the bearing. Since it acts as oil, the bearing can be cooled without having a complicated oil supply mechanism.

In the present invention, the inner ring may have a circumferential groove on the width surface, and the discharge port may be opened facing a portion of the width surface of the inner ring where the circumferential groove is provided.
When a circumferential groove is provided on the inner ring width surface, the lubricating oil discharged from the discharge port is collected in the circumferential groove, and part of it flows from the inclined surface of the inner ring to the raceway surface. Lubricating oil can be supplied.

  The gap between the flange portion of the lubricating oil introduction member and the slope portion of the inner ring may be a minute gap that regulates the flow rate of the lubricating oil. In the case of this configuration, since the flow rate of the lubricating oil flowing through the minute gap can be adjusted by the gap amount, the oil supply amount can be adjusted with a simple structure.

  The lubricating oil introduction member may be a ring-shaped outer ring spacer provided in contact with the width surface of the outer ring. If the lubricating oil introduction member also serves as an outer ring spacer, it is not necessary to provide a special member as the lubricating oil introduction member, and the configuration can be simplified.

  The lubricating oil introducing member may have a drain oil passage that penetrates from the inner diameter surface to the outer diameter surface at a position away from the discharge port in the circumferential direction. Even if a dedicated oil drain passage is not provided, the remaining lubricating oil except for the inflow into the gap between the slope portion and the bowl-like portion is appropriately discharged from the peripheral gap. However, by providing the lubricating oil discharge passage, it is possible to increase the efficiency of discharging the lubricating oil or to regulate the flow of the discharged lubricating oil. In addition, by providing an oil drainage path at a position away from the discharge port in the circumferential direction as described above, the path until lubricating oil that is not used for bearing lubrication flows into the oil drainage path becomes longer, so that the cooling efficiency is increased accordingly. Can be raised.

The lubricating oil introduction member may have a groove-like oil drain passage extending in a radial direction on a surface in contact with the width surface of the outer ring.
In the case of this configuration, the lubricating oil once supplied into the bearing, including the lubricating oil used for lubrication and the lubricating oil that has not reached the raceway surface, is discharged from the groove-like oil drain passage. For this reason, it is possible to improve the discharge performance of the lubricating oil supplied into the bearing, and to prevent the dirty lubricating oil from accumulating in the bearing.

  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 for lubrication, and the lubricating oil introduction member opens facing the width surface of the inner ring. The inner ring raceway has a discharge port, the outer ring surface of the inner ring has a larger diameter on the raceway side of the inner ring, and the lubricating oil discharged from the discharge port is subjected to centrifugal force and surface tension acting on the lubricating oil. A slope portion that leads to the surface is provided, and a flange-like portion that covers the slope portion through a gap and guides the lubricant flowing from the gap to the raceway surface is provided on the lubricant introduction member, and the flange-like portion is a rolling element. The inner diameter surface of the cage-like portion side of the cage is a tapered surface having a large diameter at the center in the width direction, so that power loss is reduced regardless of the bearing size. High speed operation without increasing, and efficiency Ku lubricating oil can guide the track surface, and can be cooled bearing without a complicated oil supply mechanism.

  A first embodiment of the present invention will be described with reference to FIGS. FIG. 1A shows a cross-sectional view of the rolling bearing of this embodiment. The lubricating device for the rolling bearing 1 supplies a part of the cooling oil discharged from the lubricating oil introducing member 7 into the rolling bearing 1 as lubricating oil. The rolling bearing 1 is formed of an angular ball bearing, and a plurality of rolling elements 4 are interposed between raceway surfaces 2 a and 3 a of the inner ring 2 and the outer ring 3. The rolling element 4 is a ball and is held by a cage 5.

  The inner diameter surface of the cage 5 is a tapered surface 5a having a large diameter at the center in the width direction. The cage 5 is an outer ring guide type, and its material is preferably bake, PEEK, C / C composite, aluminum alloy, Ti alloy (strength improvement at high speed) or the like. The material of the inner ring 2 is, for example, carburized steel in consideration of a large fitting hoop stress at high speed. The rolling element 4 is preferably made of ceramic from the viewpoint of reducing centrifugal force.

A circumferential groove 6 that is recessed in the axial direction is formed on the width surface of the inner ring 2 on the side opposite to the load (bearing rear side) in the rolling bearing 1. Further, the outer diameter surface following the raceway surface 2a on the side where the circumferential groove 6 of the inner ring 2 is formed is a slope portion 2b having a larger diameter on the raceway surface 2a side. The minimum value of the inclination angle α of the slope portion 2b is set to the value of the following formula.
α ≧ 0.0667 × dn × 10 ⁻⁴ −1.8333
Where dn is the product of the bearing inner diameter (mm) and the rotational speed (min ⁻¹ ).
According to this equation, when the rolling bearing 1 is an angular ball bearing having a bearing inner diameter of 70 mmφ and a rotation speed of 300,000 min ⁻¹ , the inclination angle α of the inclined surface portion 2b is:
α ≧ 12.8 °
It is said.

  The maximum value of the inclination angle α is preferably α ≦ 25 ° in an angular ball bearing. In the case of an angular contact ball bearing, when the inclination angle α exceeds 25 °, the radial width of the inner ring end face on the side where the inclined surface portion 2b is provided becomes narrower, and the contact area with the inner ring spacer 16 and the like with which this end face comes into contact is reduced. This is because a large axial load cannot be received. When the rolling bearing 1 is an angular ball bearing, the outer diameter surface of the portion where the step surface of the inner ring 2 is provided is the inclined surface portion 2b.

The lubricating oil introduction member 7 is a ring-shaped outer ring spacer provided adjacent to the rolling bearing 1 in the axial direction by contacting the width surface of the outer ring 3, and is provided with the circumferential groove 6 on the width surface of the inner ring 2. And an oil supply passage 9 communicating with the discharge port 8. The cooling oil supplied to the oil supply passage 9 and discharged from the discharge port 8 is sprayed to the circumferential groove 6 of the inner ring, and a part thereof is centrifugal force and surface tension, and the slope portion 2b from the inner diameter surface of the circumferential groove 6 Flows along the raceway surface 2a of the inner ring 2 as a lubricating oil.
FIG. 2 is a front view of the lubricating oil introduction member 7 as viewed from the bearing arrangement side. In this example, the oil supply path 9 and the discharge port 8 communicating with the oil supply path 9 are made one. However, the present invention is not limited to this, and a plurality of oil supply paths 9 are arranged separately in the circumferential direction of the lubricating oil introduction member 7 so as to increase the lubrication efficiency. Anyway.

  The diameter of the discharge port 8 is preferably smaller from the viewpoint of increasing the jet speed of the discharged oil. The length of the straight portion of the discharge port 8 is preferably about 4 times the diameter of the discharge port from the viewpoint of preventing the discharge oil from diffusing. The angle of the discharge port 8 with respect to the inner ring end surface on the circumferential groove 6 side may be arbitrary.

  As shown in FIG. 1, the lubricating oil introduction member 7 extends in the axial direction from the side surface toward the bearing 1, and covers the slope portion 2 b of the inner ring 2 via a gap δ (FIG. 1B). It has a bowl-shaped portion 10 for guiding the lubricating oil flowing from the gap δ to the raceway surface 2a. The hook-like portion 10 extends to the inner diameter side of the cage 5. In this embodiment, the inner diameter surfaces 5a on both sides of the cage 5 sandwiching the pockets are the tapered surfaces described above. However, the present invention is not limited to this, and only the inner diameter surface 5a on the side where the flange-shaped portion 10 extends is tapered. It may be a surface. A corner portion where the width surface of the inner ring 2 facing the discharge port 8 and the slope portion 2b intersect with each other is a curved surface portion 2ba having an arcuate cross section. The reason why the curved surface portion 2ba is used is to prevent the lubricating oil from leaving the inner ring 2 by centrifugal force from the corner portion. 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 internal damage and improving the handleability.

  Of the lubricating oil discharged from the discharge port 8, the remaining lubricating oil excluding the inflow flowing into the minute gap δ is discharged to the outside from the lubricating oil discharge path 11. The lubricating oil discharge path 11 includes an oil draining path 12 provided in the lubricating oil introducing member 7, a grooved oil draining path 13, and an oil draining groove of an outer ring spacer 15 disposed in contact with the load side of the inner ring 2. 14 or the like. The oil discharge passage 12 of the lubricating oil introducing member 7 is formed so as to penetrate from the inner diameter surface to the outer diameter surface at a position away from the discharge port 8 in the circumferential direction (here, at a position 180 ° away from the discharge port 8). Has been. Note that a plurality of oil drain passages 12, groove-like oil drain passages 13, and oil drain grooves 14 may be provided in the circumferential direction.

The inner diameter surface of the lubricating oil introducing member 7 is a step surface 7a in which a part of the axial direction facing the inner ring 2 is larger in diameter than the remaining portion except for the portion where the discharge port 8 is formed. The oil drain passage 12 is open at 7a. Further, the groove-like oil discharge passage 13 of the lubricating oil introduction member 7 is formed to extend in the radial direction on a part of the surface in contact with the width surface of the outer ring 3. The oil draining groove 14 of the outer ring spacer 15 is formed to extend in the radial direction in a part of the end surface that is in contact with the outer ring 3.
The cooling oil to be used preferably has an ISO viscosity of 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

  The operation of the lubricating device having the above configuration will be described. The cooling oil pumped to the oil supply passage 9 of the lubricating oil introduction member 7 is discharged from the discharge port 8 and sprayed to the formation location of the circumferential groove 6 on the width surface of the inner ring 2 that faces the cooling oil. A part of the cooling oil sprayed on the circumferential groove 6 is separated from the inner wall surface on the outer diameter side of the circumferential groove 6 in the inner ring 2 by the surface tension and the centrifugal force acting on the cooling oil as the inner ring 2 rotates. It flows as lubricating oil into the raceway surface 2a of the inner ring 2 along the slope portion 2b. In this way, the cooling oil discharged from the discharge port 8 is collected in the circumferential groove 6, and a part thereof flows from the inclined surface portion of the inner ring to the raceway surface, so that the lubricating oil is evenly distributed over the entire circumference of the raceway surface 2a. Can supply. The lubricant is smoothly transferred from the inner wall surface of the circumferential groove 6 to the slope portion 2b by appropriately balancing the surface tension of the lubricant, the centrifugal force acting on the lubricant, and the slope angle of the slope portion 2b. It is possible to prevent the lubricating oil from being scattered by centrifugal force. Here, since the intersecting portion between the width surface of the inner ring 2 and the slope portion 2b is the curved portion 2ba, the lubricating oil moves to the slope portion 2b more smoothly.

The slope portion 2b of the inner ring 2 is covered with the flange portion 10 of the lubricating oil introduction member 7 through the gap δ, and the lubricant oil flowing from the gap δ to the raceway surface 2a is guided by the flange portion 10. The lubricating oil flowing in the gap δ is pressed against the inner diameter surface 5a side of the bowl-shaped portion 10 by the action of centrifugal force, without being a flow adhering to the inclined surface portion 2b due to various conditions such as rotational speed and inclination angle. May flow in a wet state. The lubricating oil that flows in this state falls off to the outer diameter side by centrifugal force at the point where the tip of the bowl-shaped portion 10 is exited. However, since the hook-shaped portion 10 extends to the inner diameter side of the cage 5 and the inner diameter surface 5a of the cage 5 is a tapered surface having a large diameter at the center in the width direction, the tip of the cage-shaped portion 10 The lubricating oil that has flowed down from the outer diameter side to the outer diameter side is received by the tapered inner diameter surface 5 a of the cage 5 and supplied to the rolling elements 4. For this reason, the lubricating oil supplied to the gap δ between the inclined surface portion 2b of the inner ring 2 and the flange-shaped portion 10 of the lubricating oil introducing member 7 is used for lubrication without waste.
If the gap δ is a minute gap narrower than the oil film of the lubricating oil flowing along the inclined surface portion 2b, the flow rate can be adjusted by this gap δ, so that the cooling oil flow rate to the oil supply passage 9 is externally adjusted. Without adjustment, the flow rate of the lubricating oil flowing through the minute gap δ can be easily adjusted.

  The remaining lubricating oil excluding the inflow that flows into the minute gap δ is discharged from the oil drain passage 12, the groove-like drain passage 13 and the outer ring spacer 15 of the lubricant introduction member 7 constituting the lubricant drain passage 11. It is discharged to the outside through an oil groove 14 by a drain oil pump (not shown). The rolling bearing 1 is effectively cooled by the lubricating oil as the cooling oil discharged through such a path.

This rolling bearing lubrication device guides and supplies the lubricating oil discharged from the lubricating oil introducing member 7 through a gap δ between the inclined surface portion 2b of the inner ring 2 and the flange portion 10 covering the inclined surface portion 2b. Therefore, a large stirring resistance does not occur, and high speed operation is possible without increasing power loss. In addition, since the lubricating oil is guided by the gap δ between the inner ring inclined surface portion 2b and the bowl-shaped portion 10, unlike the case of forming a minute gap with the width surface of the inner ring 2, when the bearing size is small or the thickness of the inner ring 2 is It can be applied even when it is thin.
In this embodiment, the lubricating oil discharged from the discharge port 8 of the lubricating oil introduction member 7 is received by the inner peripheral groove 6 on the width surface of the inner ring 2, and the lubricating oil is moved from the inner wall surface to the slope portion 2b. However, even when the inner circumferential groove 6 is not provided in the width surface of the inner ring 2, the lubricating oil sprayed from the discharge port 8 to the width surface of the inner ring 2 is moved from the inner ring width surface to the slope portion 2b by centrifugal force and surface tension. Can be made.

  The remaining lubricating oil excluding the inflow flowing into the gap δ is drained from the drain oil passage 12, the groove-like drain passage 13 and the outer ring spacer 15 of the lubricant introduction member 7 constituting the lubricant drain passage 11. Since the rolling bearing 1 is effectively cooled by discharging to the outside through the groove 14, the rolling bearing 1 can be cooled without having a complicated oil supply mechanism.

  Since the lubricating oil introducing member 7 is a ring-shaped outer ring spacer provided in contact with the width surface of the outer ring 3, it is not necessary to provide a special member as the lubricating oil introducing member 7, and the configuration can be simplified.

  Since the lubricant introduction member 7 has a drain oil passage 12 that penetrates from the inner diameter surface to the outer diameter surface at a position away from the discharge port 8 in the circumferential direction, lubricant oil that is not used for bearing lubrication is drained. The path to flow into the path 12 becomes longer, and the cooling efficiency can be increased accordingly.

  Further, the lubricant introduction member 7 has a groove-like oil passage 13 extending in the radial direction on the surface in contact with the width surface of the outer ring 3, separately from the oil passage 12, and therefore, a lubricant oil outflow route that is not used for bearing lubrication. This increases the cooling efficiency.

  FIG. 3 shows another embodiment of the present invention. In the first embodiment shown in FIG. 1 and FIG. 2, the rolling bearing lubrication device of this embodiment is configured to retract the width surface on the slope portion 2 b side of the inner ring 2 to the inside of the bearing relative to the corresponding width surface of the outer ring 3. The width of the inner ring 2 is shortened. Correspondingly, the portion where the discharge port 8 and the flange-shaped portion 10 are formed on the side surface of the lubricating oil introducing member 7 is projected to the inside of the bearing. Other configurations are the same as those in the first embodiment.

  In the case of this embodiment, it is possible to reduce the reduction in the radial width of the inner ring end surface on the side where the inclined surface portion 2b is provided by reducing the width dimension on the side where the inclined surface portion 2b of the inner ring 2 is formed. The contact area with the inner ring spacer 16 and the like in contact with each other is not reduced, and a large axial load can be received.

  FIG. 4 shows an example of a spindle device provided with the bearing device of the rolling bearing of the first embodiment shown in FIGS. 1 and 2. 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 plurality of (here, two) rolling bearings 1 separated in the axial direction. 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 housing 26. These inner and outer rings 2 and 3 are fixed in the housing 26 by an inner ring retainer 27 and an outer ring retainer 28. The housing 26 has a double structure of an inner peripheral housing 26A and an outer peripheral housing 26B. An outer ring spacer 30 and a lubricant introduction member 7 are provided between the outer rings 3 of the both rolling bearings 1, and an inner ring spacer 31 is provided between the inner rings 2. At one end portion of the main shaft 25, a bearing fixing nut 32 that is pressed against the inner ring retainer 27 and fixes the rolling bearing 1 is screwed. The inner peripheral housing 26A is provided with two lubricating oil supply passages 33 communicating with the oil supply passages 9 of the respective lubricating oil introduction members 7 and one drain oil recovery passage 34. Each lubricating oil supply path 33 extends in the axial direction and opens at both end faces of the inner peripheral housing 26A. The oil recovery path 34 extends in the axial direction and penetrates the inner ring retainer 27 and the outer ring retainer 28. The oil discharge passages 12 and the grooved oil discharge passages 13 of the respective lubricating oil introduction members 7 are communicated with the oil discharge recovery passage 34. Further, in the first embodiment, the oil drain grooves 14 are formed in the outer ring spacer 15, but in this example, the oil drain grooves 14 are formed in each outer ring retainer 28, and these oil drain grooves 14 are used for the oil recovery. It is connected to the road 34.

  The lubricating device of the rolling bearing 1 receives a part of the discharged cooling oil of the cooling oil supply device 35 via the filter 36, the lubricating oil supply passage 33 and the oil supply passage 9 of the lubricating oil introducing member 7, as described above. A part of the cooling oil is supplied to the rolling bearing 1 as lubricating oil and the rest as cooling oil. Waste oil that has become cooling oil and has flowed out of the drain oil passage 12, the groove-like oil passage 13, and the oil drain groove 14 into the oil recovery passage 34 is recovered by an oil recovery pump 38 in an oil recovery tank 38, It is returned to the cooling oil supply device 35 again. The housing 26 is separately provided with an oil supply passage (not shown) for cooling the housing, and cooling oil is supplied from the cooling oil supply device 35 to the oil supply passage. The cooling oil that has cooled the housing 26 is recovered in the oil recovery tank 38 and returned to the cooling oil supply device 35 again.

(A) is sectional drawing which shows the lubricating device of the rolling bearing concerning 1st Embodiment of this invention, (B) is an enlarged view of the A section in (A). It is the front view seen from the bearing arrangement | positioning side of the lubricating oil introduction member in the lubricating device. It is sectional drawing of the lubricating device of the rolling bearing concerning other embodiment of this invention. It is a block diagram which shows the spindle apparatus provided with the lubricating device of the rolling bearing concerning 1st Embodiment of this invention, and the oil supply apparatus connected to this. It is sectional drawing of a prior art example. It is an enlarged view of the V section in FIG. It is sectional drawing which shows the modification of a prior art example. It is sectional drawing which shows the example of a proposal of the lubrication apparatus of a rolling bearing.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Rolling bearing 2 ... Inner ring 2a ... Raceway surface 2b ... Slope part 3 ... Outer ring 5 ... Retainer 5a ... Inner diameter surface 6 ... Circumferential groove 7 ... Lubricating oil introduction member 8 ... Discharge port 10 ... Gutter-shaped part 11 ... Lubricating oil Discharge path 12 ... drainage path 13 ... groove-like drainage path δ ... clearance

Claims (6)

  In a rolling bearing lubrication device that discharges and lubricates lubricating oil from a lubricating oil introducing member into a rolling bearing, the lubricating oil introducing member has a discharge port that opens to face a width surface of the inner ring, and is provided outside the inner ring. On the diameter surface, a raceway surface side of the inner ring has a large diameter, and a slope portion is provided that guides the lubricating oil discharged from the discharge port to the raceway surface of the inner ring by centrifugal force and surface tension acting on the lubricating oil. A lug-like part that covers the part via a gap and guides the lubricating oil flowing from the gap to the raceway surface is provided in the lubricating oil introduction member, and the saddle-like part extends to the inner diameter side of the cage that holds the rolling elements. A rolling bearing lubrication device, wherein an inner diameter surface of the cage on the side of the flange-shaped portion is a tapered surface having a large diameter in the center in the width direction.   2. The lubrication of a rolling bearing according to claim 1, wherein the inner ring has a circumferential groove on the width surface, and the discharge port is opened facing a portion of the width surface of the inner ring where the circumferential groove is provided. apparatus.   The rolling bearing lubrication device according to claim 1 or 2, wherein a gap between the flange portion and the slope portion of the inner ring is a minute gap that regulates a flow rate of the lubricating oil.   4. The lubricating device for a rolling bearing according to claim 1, wherein the lubricating oil introducing member is a ring-shaped outer ring spacer provided in contact with a width surface of the outer ring. 5.   The rolling bearing lubrication device according to claim 4, wherein the lubricating oil introduction member has an oil drain passage penetrating from the inner diameter surface to the outer diameter surface at a position away from the discharge port in the circumferential direction. 6. The rolling bearing lubrication device according to claim 4 or 5, wherein the lubricating oil introduction member has a groove-like oil drain passage extending in a radial direction on a surface in contact with a width surface of the outer ring.

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