JP2007247783A - Lubricating structure of roller bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide lubricating structure for a roller bearing, which secures lubrication of sliding parts between a roller end face and an inner ring collar over a whole circumference of the bearing, and does not cause starvation of scarce lubricating oil so as to be suitable for high-speed operation. <P>SOLUTION: A receiving groove 10 receiving the lubricating oil supplied from the outside of the bearing is disposed to an end face of an inner ring large collar 2b of a tapered roller bearing 1, and a communication hole 11 connecting the receiving groove 10 with an end part of a raceway surface 2a of an inner ring 2. The inner ring 2 is split into a collar ring 22 constituting the large collar 2b and an inner ring main body 21 constituting the raceway surface 2a, and the receiving groove 10 and the communication hole 11 are disposed to the collar ring 22. An enlarged diameter part 28 abutted with the end face of the large collar 2b of the inner ring 2 is disposed to a shaft 24 in which the inner ring 2 is fitted onto the outer circumference thereof. An outer diameter of a stepped face 28b of the enlarged diameter part 28 abutted with the end face of the large collar 2b is smaller than a diameter of the receiving groove 10, an outer peripheral face of the enlarged part 28 is formed to be an inclined face 28a in which a large collar 2b side thereof is larger in diameter. An air oil supply means 8b discharging air oil is disposed to the inclined face 28a. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

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

Angular ball bearings are mainly used to support high-speed spindles such as spindles for machine tools in order to suppress heat generation of the bearings. However, although angular ball bearings are suitable for high-speed rotation, the bearing rigidity is lower than that of roller bearings.Therefore, when a large external force is applied to the spindle end, such as heavy cutting, the deflection of the spindle increases, and the It is difficult to improve the shape accuracy of the work.
There is also an example in which a cylindrical roller bearing is disposed at the end of the main shaft to improve radial rigidity and an angular ball bearing that receives an axial load is used in combination. In this case, since the assembly width of the bearing becomes large, the main shaft becomes long and it is difficult to make it compact.

  Tapered roller bearings that can simultaneously apply radial and axial loads are available as bearings that can improve the rigidity and compactness of the spindle. An example of a spindle device using a tapered roller bearing is shown in FIG. 5, and an enlarged sectional view of the bearing portion is shown in FIG. For the lubrication of the bearing in this spindle device, air oil lubrication effective for high-speed operation by supplying a trace amount of oil is employed. Specifically, on the back side of the tapered roller bearing 41, the inner diameters of the inner ring collar 42c and the cage 45 are passed from the air oil supply devices 50A and 50B of FIG. Air oil is supplied between the tapered roller 44 and the raceway surface 42a of the inner ring 42 and between the tapered roller 44 and the retainer 45 by supplying air oil between them. Further, on the front side of the tapered roller bearing 41, the inner ring large collar 42b and the inner diameter surface of the cage 45 are passed through the air oil supply passages 52 of the bearing housing 51 from the air oil supply devices 50A and 50B of FIG. Lubricating between the roller large end surface and the inner ring large collar surface, which is the guide surface, is performed by blowing air oil from the nozzle 54 to the large end surface of the tapered roller 44.

The problem when the tapered roller bearing is operated at high speed is the lubrication of the sliding portion between the roller large end surface with relatively large slippage between the tapered roller and the raceway surface and the inner ring large collar surface that guides this. . As the lubrication technology, the following two have been proposed.
(1) By providing a guide rod in sliding contact with the large end surface of the tapered roller on the outer ring side, lubricating oil supplied from the small end surface side of the tapered roller is secured on the guide surface of the guide roller ( Patent Document 1).
(2) The lubricating oil is forcibly supplied from the outside to the guide surface of the inner ring large collar by connecting the outer oil filling section and the inner ring large collar section through the oil hole provided in the inner ring (Patent Document 2). ).
Japanese Patent Publication No.53-8856 JP-A-8-270660

In the lubrication technique disclosed in Patent Document 1, an oil drain hole is provided in the outer ring in order to suppress agitation resistance due to stagnant oil at the outer ring guide rod. There is a problem that it is difficult to set the number of holes.
In addition, the lubricating technique disclosed in Patent Document 2 has a problem in that the structure is complicated although the lubricating oil does not stay.
In the structure in which lubricating oil is supplied from a plurality of nozzles or oil supply holes distributed on the circumference of the bearing, as in the lubricating technique shown in FIGS. 5 and 6 and the lubricating technique disclosed in Patent Document 2. Since the tapered roller revolves while rotating, the amount of lubricating oil adhering to the roller large end surface varies depending on where the tapered roller is located on the circumference. Also, the lubricating oil discharged from the nozzle or oil supply hole and adhering to the roller large end surface decreases with the revolution of the tapered roller, and after one revolution, the roller large end surface is positioned on the circumference facing the nozzle and oil supply hole. Immediately before reaching the roller, the lubricating oil on the roller large end face is in a lean state. That is, the roller large end face is in a thin starvation state of the lubricating oil, that is, a deficient state, making it difficult to secure an oil film on the sliding portion.

  It is an object of the present invention to ensure lubrication of the sliding portion between the roller end face and the inner ring flange over the entire circumference of the bearing, and lubrication of the roller bearing suitable for high-speed operation that does not cause a thin starvation of lubricating oil at the sliding portion. Is to provide a structure.

In the lubricating structure of the roller bearing according to the present invention, a receiving groove for receiving lubricating oil supplied from the outside of the bearing is provided on the end face of the inner ring rod of the roller bearing, and the communication hole communicates from the receiving groove to the end of the raceway surface of the inner ring. Is provided.
According to this configuration, the lubricating oil supplied from the outside of the bearing accumulates in the receiving groove provided on the end surface of the inner ring rod, and is directed toward the roller guide surface of the inner ring rod through the communication hole due to the centrifugal force accompanying the rotation of the bearing. Since it is discharged and used for lubrication of the sliding portion with the roller end surface, the lubricating oil can be evenly distributed over the roller end surface of the entire circumference of the bearing. As a result, the roller bearing can be applied to a thin starvation of the lubricating oil between the inner ring and the end face where the lubrication conditions are severe with slipping, that is, a high speed operation in which a deficiency does not occur.
Further, since there is no wind noise as in the case of the conventional example in which air oil is directly injected to the rollers or the cage using the nozzle, the noise can be reduced.

  In this invention, an inner ring | wheel may be divided | segmented into the collar ring which comprises the said inner ring collar, and the inner ring main body which comprises a track surface, and the said receiving groove and the communicating hole may be provided in the said collar ring. In this configuration, it is easy to form the receiving groove and the communication hole in the inner ring.

In this invention, the shaft on which the inner ring is fitted to the outer periphery is provided with an enlarged diameter portion that comes into contact with the end surface of the inner ring rod of the inner ring, and the outer diameter of the stepped surface that comes into contact with the end surface of the inner ring rod of the enlarged ring portion is received. The outer diameter of the enlarged diameter portion may be formed on a slope having a larger diameter on the inner ring flange side, and air oil supply means for discharging air oil may be provided on the slope.
In this configuration, the air oil discharged from the air oil supply means collides with the inclined surface of the enlarged diameter portion of the shaft. At this time, the oil in the air oil expands the shaft due to the centrifugal force and the surface tension of the oil accompanying the rotation of the bearing. It moves on the slope of the diameter part and scatters in the circumferential direction from the end part on the large diameter side and accumulates in the receiving groove. Therefore, the oil can be smoothly supplied to the receiving groove.

  In this invention, you may provide the air oil supply means which discharges air oil to the inner diameter side part rather than the said receiving groove in the said receiving groove or the end surface of the said inner ring | wheel ring. In the case of this configuration, a route for supplying the lubricating oil to the receiving groove through the outer periphery of the shaft enlarged portion can be omitted.

  In this invention, the end surface of the inner ring rod is formed as a stepped surface with an outer diameter side protruding in the axial direction, and the receiving portion is formed on an inward circumferential surface between a large diameter side portion and a small diameter side portion of the inner ring rod. A groove may be provided.

In this invention, the roller bearing may be a tapered roller bearing, and the inner ring rod provided with the receiving groove may be a large rod. When the inner ring collar is a collar ring as described above, this large collar is the collar ring.
Tapered roller bearings impose an axial load, so that the lubrication conditions between the inner ring large end surface and the end surface are severe, which is an important issue when the lubrication rotates at high speed. Therefore, in the present invention, the lubrication of the sliding portion between the roller end surface and the inner ring rod can be ensured over the entire circumference of the bearing, and the effect that the lubricating oil does not cause a thin starvation in the sliding portion is more effectively achieved. Demonstrated.

  In the lubricating structure of the roller bearing according to the present invention, a receiving groove for receiving lubricating oil supplied from the outside of the bearing is provided on the end face of the inner ring rod of the roller bearing, and the communication hole communicates from the receiving groove to the end of the raceway surface of the inner ring. Therefore, the lubrication of the sliding part between the roller end face and the inner ring rod can be ensured over the entire circumference of the bearing, and the high speed that does not cause dilute lubrication of the lubricating oil between the inner ring flange and the end surface where the lubrication conditions are severe due to slippage. It will be suitable for driving.

  An embodiment of the present invention will be described with reference to FIGS. FIG. 1 shows an example of a high-speed spindle device having a roller bearing lubrication structure of this embodiment, and shows an example in which a tapered roller bearing is used as a roller bearing. The spindle device 23 is applied to a machine tool, and a tool or workpiece chuck is attached to the front (machining side) end of the spindle 24. The main shaft 24 is supported by a plurality (two in this case) of tapered roller bearings 1 separated in the axial direction. The inner ring 2 of each tapered roller bearing 1 is fitted to the outer diameter surface of the main shaft 24, and the outer ring 3 is fitted to the inner diameter surface of the bearing box 25. As for the tapered roller bearing 1 on the front side of the main shaft, the inner ring 2 is supported by the step surface 26a of the enlarged diameter portion 26 formed integrally with the main shaft 24, and the outer ring 3 is supported by the holding lid 27A via the first outer ring spacer 6. It is fixed in the box 25. As for the tapered roller bearing 1 on the rear side of the main shaft, the inner ring 2 is fixed in the bearing box 25 by the enlarged diameter portion 28 of the main shaft 24, and the outer ring 3 is fixed by the holding lid 27B through the first outer ring spacer 6. Yes. The enlarged diameter portion 28 on the rear side of the main shaft is constituted by an inner ring positioning spacer which is a ring component manufactured separately from the main shaft 24 and fitted to the main shaft 24. The bearing box 25 has a double structure of an inner peripheral bearing box 25A and an outer peripheral bearing box 25B, and a cooling groove 29 is formed between the inner and outer bearing boxes 25A and 25B. A second outer ring spacer 7 is disposed on the back side of the outer ring 3 of both tapered roller bearings 1, and an inner peripheral bearing box 25 </ b> A is interposed between the outer ring spacers 7. An inner ring spacer 30 is interposed between the inner rings 2 of the both tapered roller bearings 1. A bearing fixing nut 31 that presses against the inner ring positioning spacer 28 and fixes the tapered roller bearing 1 is screwed to the rear end portion of the main shaft 24.

  The holding lids 27A and 27B are provided with air oil introduction holes 33 for introducing air oil from air oil supply devices 32A and 32B, which are lubricating oil supply sources when the tapered roller bearing 1 is lubricated with air oil, respectively. Is in communication with an air oil supply path 34 provided in the inner peripheral bearing box 25A. In addition, oil pressure holes 35 are provided in the presser lids 27A and 27B, and these oil pressure holes 35 communicate with an oil drain passage 36 provided in the inner peripheral bearing box 25A. In air oil lubrication, lubricating oil is mixed with carrier air and supplied.

  The roller bearing lubrication structure in the spindle device 23 is an oil supply for supplying air oil to the tapered roller bearing 1 adjacent to the front side and the back side of the tapered roller bearing 1 as shown in a sectional view in FIG. Two outer ring spacers 6 and 7 each having paths 8 and 9 are arranged. The oil supply passages 8 and 9 of the outer ring spacers 6 and 7 communicate with the air oil supply passage 34 of the inner peripheral bearing box 25A. The tapered roller bearing 1 is a single-row tapered roller bearing having an inner ring 2, an outer ring 3, and tapered rollers 4 that are rolling elements interposed between the inner and outer rings 2 and 3. The inner ring 2 has a raceway surface 2a which is a conical surface on the outer diameter surface, and has an inner ring rod having a large rod 2b and a small rod 2c on the large diameter side and the small diameter side of the outer diameter, respectively. The outer ring 3 has a raceway surface 3 a that is a conical surface on the inner diameter surface facing the raceway surface 2 a of the inner ring 2. A plurality of tapered rollers 4 are interposed between the raceway surfaces 2a and 3a so as to freely roll. These tapered rollers 4 are held by a cage 5 at a predetermined interval in the circumferential direction.

  The inner ring 2 is divided into an inner ring main body 21 constituting the raceway surface 2a and a collar ring 22 constituting the inner ring large collar 2b. The inner ring 2 may be formed by integrating the inner ring main body 21 and the collar ring 22. The tapered roller bearing 1 shown in FIG. 2A is disposed on the rear side of the main shaft in the spindle device 23 shown in FIG. 1, and the collar ring 22 has an enlarged diameter portion 28 formed of an inner ring positioning spacer of the main shaft 24. The end face 28b is pressed. In the case of the tapered roller bearing 1 arranged on the front side of the main shaft in the spindle device 23 of FIG. 1, the step surface 26 a of the enlarged diameter portion 26 formed integrally with the main shaft 24 is pressed against the collar ring 22. As shown in FIG. 2B, which is an enlarged view of a part of FIG. 2A, the outer peripheral surface of the enlarged diameter portion 28 of the main shaft 24 is formed on an inclined surface 28a having a large diameter on the side contacting the collar ring 22. Has been. A V-shaped groove 19 having a V-shaped cross section extending in the circumferential direction is formed over the entire circumference on the slope 28a.

  The two outer ring spacers 6 and 7 are attached to an inner peripheral bearing box 25A to which the outer ring 3 of the bearing 1 is attached. The first outer ring spacer 6 provided on the front side of the bearing 1 is disposed at a position where the inner peripheral surface thereof faces the outer peripheral surface of the enlarged diameter portion 28 of the main shaft 24. The inner peripheral surface of the outer ring spacer 6 is formed on the inclined surface 6a having the same inclination angle α as the inclined surface 28a of the main shaft expanded portion 28 so that a predetermined gap is formed between the inner ring surface 6 and the inclined surface 28a of the main shaft expanded portion 28. . The oil supply passage 8 of the outer ring spacer 6 includes a large-diameter base path portion 8a extending from the outer peripheral surface of the outer ring spacer 6 toward the inner peripheral side, and a slope of the main shaft enlarged diameter portion 28 from the tip of the base path portion 8a. A small-diameter nozzle 8b extending toward the V-groove 19 of 28a and opening on the inner peripheral surface of the outer ring spacer 6; An air oil supply means 40 for discharging air oil to the V groove 19 of the inclined surface 28a of the main shaft enlarged diameter portion 28 by the oil supply passage 8 having the nozzle 8b, the air oil supply passage 34 of the inner peripheral bearing box 25A, and the air oil supply device 32B. Composed.

The collar ring 22 of the inner ring 2 has an annular receiving groove 10 for receiving the lubricating oil supplied from the inclined surface 28a of the main shaft enlarged diameter portion 28, and an end portion on the large end side of the inner ring raceway surface 2a from the receiving groove 10. A communication hole 11 communicating with the communication hole 11 is provided. Specifically, the end surface of the collar ring 22 on the side facing the outer ring spacer 6 is formed as a stepped surface whose outer diameter side protrudes in the axial direction, and the large diameter side portion and the small diameter side portion of the inner ring large collar 2b. The receiving groove 10 is provided on the inward circumferential surface between the two. The outer diameter of the step surface 28 b that contacts the end face of the collar ring of the main shaft diameter-expanded portion 28 is smaller than that of the receiving groove 10.
Further, the end face of the collar ring 22 facing the inner ring main body 21 is recessed toward the receiving groove 10 across the inner diameter side portion facing the end face of the inner ring main body 21 from the roller guide surface of the inner ring large collar 2a. An annular circumferential groove 12 is provided over the entire circumference in the circumferential direction, and the communication hole 11 is opened in the circumferential groove 12. An annular communication space 13 communicating with the communication hole 11 is formed between the circumferential groove 12 and the end surface of the inner ring main body 21. A plurality (for example, 4 to 6) of communication holes 11 are provided evenly distributed in the circumferential direction.
Further, a small spacer 14 is interposed between the first outer ring spacer 6 and the outer ring 3, and one end is provided between the small spacer 14 and the outer ring 3 and between the small spacer 14 and the outer ring spacer 6. Oil discharge holes 15A and 15B are formed on the roller large end surface side, the other end opening on the outer diameter surface side of the small spacer 14 respectively.

An annular slit component 16 is provided on the inner peripheral surface of the second outer ring spacer 7 provided on the back side of the bearing 1, and the outer peripheral surface of the slit component 16 and the inner peripheral surface of the outer ring spacer 7 are In the meantime, an annular slit 17 communicating with the oil supply passage 9 of the outer ring spacer 7 is formed. The slit 17 is disposed so as to face between the outer diameter surface of the inner ring gavel 2c and the inner diameter surface of the cage 5, and the air oil supplied to the oil supply passage 9 from the air oil supply passage 34 of the inner peripheral bearing box 25A. Is discharged from the slit 17 toward the inner diameter side of the cage 5. The oil supply passage 9 of the second outer ring spacer 7 extends from the outer peripheral surface of the outer ring spacer 7 toward the inner peripheral side and opens into a circumferential groove 18 formed over the entire inner peripheral surface of the outer ring spacer 7. The slit 17 communicates with the oil supply passage 9 through the circumferential groove 18.
The second outer ring spacer 7 has an oil drain hole 15 </ b> C having one end opened on the roller small end face side and the other end opened on the outer peripheral surface of the outer ring spacer 7. Air oil provided as lubricating oil in the bearing 1 is externally supplied from the oil drain holes 15A to 15C provided in the outer ring spacers 6 and 7 through the oil drain passage 36 (FIG. 1) of the inner peripheral bearing box 25A. To be discharged.

  The lubrication structure for the tapered roller bearing 1 on the front side of the main shaft 24 is different from the lubrication structure for the tapered roller bearing 1 on the rear side, except that the main shaft enlarged diameter portion 26 is integrated with the main shaft 24 or separate. Since it is the same, the overlapping description is omitted.

  The operation of the lubricating structure of the roller bearing will be described. 2A and 2B, the flow of air oil supplied into the bearing 1 is indicated by arrows. The air oil supplied from the air oil supply devices 32A and 32B reaches the oil supply passages 8 and 9 of the two outer ring spacers 6 and 7 via the air oil supply passage 34 of the bearing box 25.

  On the front side of the tapered roller bearing 1, air oil that has reached the oil supply passage 8 of the first outer ring spacer 6 is injected by the nozzle 8b. The injected air oil collides with the inclined surface of the V groove 19 on the inclined surface 28 a of the main shaft enlarged diameter portion 28, and at this time, the oil in the air oil adheres to the inclined surface of the V groove 19. The oil adhering to the inclined surface of the V-groove 19 moves to the inclined surface 28a of the main shaft enlarged portion 28 while adhering to the inclined surface of the V-groove 19 due to the centrifugal force accompanying the rotation of the bearing 1 and the surface tension of the oil. Spatter in the circumferential direction from the radial end. Since the receiving groove 10 of the collar ring 22 is disposed on the outer diameter side, the scattered oil accumulates in the receiving groove 10. In this way, the lubricating oil is smoothly supplied from the oil supply passage 8 of the first outer ring spacer 6 to the receiving groove 10. The inclination angle α of the inclined surface 28a of the main shaft enlarged portion 28 is set in accordance with the operating rotational speed of the bearing 1. For example, when the maximum rotational speed to be used is 10,000 rpm, it is set to 10 ° or more. desirable. The V-groove 19 has an annular shape over the entire circumference of the main shaft enlarged diameter portion 28, and serves as a pressure release space for the jet air from the nozzle 8b.

  The oil stored in the receiving groove 10 moves to the circumferential groove 12 through the communication hole 11 due to the centrifugal force accompanying the rotation of the bearing 1. The oil moved to the circumferential groove 12 is discharged radially from the inner diameter side end of the circumferential groove 12 toward the roller guide surface of the inner ring large collar 2b, and is used for lubrication of the sliding portion with the roller large end surface. Since a plurality of the communication holes 11 are equally distributed in the circumferential direction, the discharged oil from the circumferential groove 12 can be evenly distributed to the roller large end surface of the entire circumference of the bearing.

  Thus, since oil is supplied from the entire circumference of the circumferential groove 12 to the roller large end face, uneven lubrication on the circumference as in the case of the conventional example in which the nozzle is supplied to the roller end face is eliminated, and the lubricating oil Therefore, the tapered star bearing 1 can be operated at high speed. Further, since there is no wind noise as in the conventional example in which air oil is directly injected into the tapered rollers 4 and the cage 5 using a nozzle, noise can be reduced.

On the back side of the tapered roller bearing 1, the air oil that has reached the oil supply passage 9 of the second outer ring spacer 7 is discharged from the annular slit 17 and enters the inner diameter portion of the cage 5, accompanying the rotation of the inner ring 2. Oil adheres to the raceway surface 3a of the outer ring 3 by the air flow generated by the pumping action in the bearing. As a result, the raceways 2a and 3a of the inner and outer rings 2 and 3 are lubricated. The air oil used for lubrication on the front side and the back side of the tapered roller bearing 1 is discharged from the oil drain holes 15A to 15C provided in the outer ring spacers 6 and 7 through the oil drain passage 36 of the bearing box 26 to the outside. Discharged.
Thus, since air oil is discharged from the entire circumference of the annular slit 17 also on the back side of the tapered roller bearing 1, it is possible to suppress the occurrence of lean starvation of the lubricating oil also on the inner and outer ring raceway surfaces 2a and 3a.
In this embodiment, the inner ring 2 is divided into a collar ring 22 constituting the large collar 2b and an inner ring body 21 constituting the raceway surface 2a, and the receiving groove 10 and the communication hole 11 are provided in the collar ring 22. Therefore, it is easy to form the receiving groove 10 and the communication hole 11 in the inner ring 2.

FIG. 3 shows a partially enlarged view of another embodiment. In the embodiment shown in FIG. 2, the lubrication structure of this roller bearing includes the nozzle 8 b of the oil supply passage 8 in the first outer ring spacer 7, the receiving groove 10 of the collar ring 22 of the inner ring 2, or the outer ring spacer of the collar ring 22. 7, the outer peripheral surface of the main shaft enlarged diameter portion 28 is not a slope. As in the first embodiment, the oil supply path 41 having the nozzle 8b, the air oil supply path 34 of the inner peripheral bearing box 25A (FIG. 2), and the air oil supply device 32B constitute an air oil supply means 41. Other configurations are the same as those in FIG.
In the case of this embodiment, the nozzle 8b directly discharges air oil toward the receiving groove 10 of the collar ring 22 or the end face of the collar ring 22 facing the outer ring spacer 7, so that the spindle expansion in the first embodiment is performed. The diameter portions 26 and 28 are not necessary.

  FIG. 4 shows a lubricating structure of a roller bearing according to still another embodiment. In this embodiment, the tapered roller bearing 1 in the first embodiment shown in FIG. 2 is a cylindrical roller bearing 1A. The cylindrical roller bearing 1A has inner ring rods 2Ab on both sides of the inner ring 2A. The inner ring 2A is divided into a pair of collar rings 22A constituting the inner ring rod 2Ab on both sides and an inner ring main body 21A constituting the raceway surface 2a. The receiving grooves 10 are provided on the end surfaces of the inner ring rods 2Ab on both sides in the same manner as in the above-described embodiment, and the communication holes 11 communicating from the receiving grooves 10 to the ends of the raceway surface 2a of the inner ring 2A are provided. Further, on both sides of the cylindrical roller bearing 1A, an outer ring spacer 6 having an oil supply passage 8 and an inner ring positioning spacer 28 having an inclined surface 28a are provided as in the first embodiment. Other configurations are the same as those of the first embodiment shown in FIG. 2, and the corresponding parts are denoted by the same reference numerals and redundant description is omitted.

It is sectional drawing of the spindle apparatus provided with the lubricating structure of the roller bearing concerning one Embodiment of this invention. (A) is an expanded sectional view of the lubricating structure of the roller bearing, and (B) is a partially enlarged view of FIG. It is a partial expanded sectional view of the lubricating structure of the roller bearing concerning other embodiment of this invention. (A) is sectional drawing of the lubrication structure of the roller bearing concerning further another embodiment of this invention, (B) is the elements on larger scale of the figure (A). It is sectional drawing of the spindle apparatus provided with the lubrication structure of the conventional roller bearing. It is an expanded sectional view of the lubricating structure of the roller bearing.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Tapered roller bearing 1A ... Cylindrical roller bearing 2 ... Inner ring 2A ... Inner ring 2a ... Raceway surface 2b ... Inner ring large collar 2Ab ... Inner ring collar 8b ... Nozzle 10 ... Receiving groove 11 ... Communication hole 21 ... Inner ring main body 22 ... Collar ring 22A ... Spiral ring 24 ... main shaft 26 ... main shaft diameter-expanding portion 28 ... main shaft diameter-expanding portion 28a ... slopes 40 and 41 ... air oil supply means

Claims (6)

  A roller bearing lubrication structure in which a receiving groove for receiving lubricating oil supplied from the outside of the bearing is provided on an end face of the inner ring rod of the roller bearing, and a communication hole is provided from the receiving groove to the end of the raceway surface of the inner ring.   The roller bearing lubrication structure according to claim 1, wherein the inner ring is divided into a collar ring constituting the inner ring rod and an inner ring main body constituting a raceway surface, and the collar groove is provided with the receiving groove and the communication hole.   The diameter of the stepped surface of the enlarged diameter portion, which contacts the end surface of the inner ring rod, is provided on the shaft on which the inner ring is fitted to the outer periphery. A roller bearing lubrication structure in which the diameter is smaller than that of the receiving groove, the outer peripheral surface of the enlarged diameter portion is formed on an inclined surface having a large diameter on the inner ring flange side, and air oil supply means for discharging air oil is provided on the inclined surface.   3. The lubricating structure of a roller bearing according to claim 1, further comprising air oil supply means for discharging air oil to a portion on an inner diameter side of the receiving groove or an end surface of the inner ring rod with respect to the receiving groove.   5. The end surface of the inner ring rod according to claim 1, wherein the end surface of the inner ring rod is formed as a stepped surface with an outer diameter side protruding in the axial direction, and the inner ring rod has a large diameter side portion and a small diameter side portion. A lubrication structure for a roller bearing in which the receiving groove is provided on an inward circumferential surface therebetween. 6. The lubricating structure of a roller bearing according to claim 1, wherein the roller bearing is a tapered roller bearing, and the inner ring rod provided with the receiving groove is a large cage.

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