JP4583429B2 - Rolling bearing device - Google Patents

Description

  The present invention relates to a rolling bearing device that is forcibly lubricated by lubricating oil.

  In a rolling bearing used under high speed rotation, such as a bearing used for a spindle of a machine tool or the like, lubricating oil is injected or sprayed between an inner ring and an outer ring to lubricate the inside of the bearing. During high-speed rotation of the spindle, it is necessary to reliably supply the bearing against the high-speed air flow near the bearing end face caused by centrifugal force or rotation of rolling elements and cages. Lubrication on the inner ring raceway surface where lubrication failure is likely to occur has been a problem.

  Conventionally, various types of so-called under-lace lubrication, in which lubricating oil is jetted from an oil supply hole having an opening on an inner ring raceway surface formed in an inner ring toward a rolling element, are known as bearing lubrication for lubricating the inside of the bearing. It has been. As a specific example of this underlace lubrication, for example, as in an angular bearing device shown in Patent Document 1, lubricating oil injected from a nozzle or the like is accumulated in an annular space provided in an inner ring spacer, and from this annular space, Similarly, there is one that injects lubricating oil toward a rolling element through an oil supply hole formed in an inner ring spacer.

In Patent Document 1, it is necessary to make the outlet of the oil supply hole formed in the inner ring spacer as close as possible to the rolling elements. For this reason, the axial dimension of the spacer is increased and the axial dimension of the inner ring is increased. It is significantly shorter than the axial dimension of the outer ring, and the inner ring spacer is inserted inwardly in the radial direction of the outer ring. However, such a structure has the following disadvantages (1) to (4).
(1) Since the mechanism for forming the annular space is provided in a member different from the inner ring, the structure of the bearing device is complicated and enlarged.
(2) If the axial dimensions of the inner and outer rings are greatly different, it becomes difficult to manage the difference (so-called difference width) in the axial dimension between the inner and outer rings. That is, if the difference width corresponds to the preload amount, the inner ring and the outer ring are placed on the surface plate, and the height difference may be obtained using the inner end face of the inner and outer rings as a reference plane. In the case where the inner and outer rings are placed on a jig having a step placed on a surface plate and the heights of the inner and outer rings are aligned, the difference in height with the inner end face of the inner and outer rings as the reference plane Or the outer end face of each track ring should be used as the reference plane.
(3) Since the inner ring whose axial dimension is shortened has a large amount of expansion deformation due to centrifugal force, the fitting to the main shaft is loosened, so that creep or the like is likely to occur. In addition, the inner ring having a short axial dimension tends to be inclined with respect to the main shaft and tends to increase misalignment.
(4) The inner ring spacer has a long axial dimension, and the inner ring side end portion is thick because an annular groove is provided. In particular, the inner ring side end portion of the inner ring spacer is expanded and deformed by centrifugal force. It becomes easy to do. Due to the expansion and deformation of the end portion of the inner ring spacer, the axial dimension of the inner ring spacer changes, and as a result, the preload amount changes.

In order to solve such problems, for example, as shown in Patent Document 2, an annular groove is provided on one end face of the inner ring for storing lubricating oil ejected from a nozzle, and the bottom of the annular groove is provided. Provided with a plurality of cooling through holes penetrating in the axial direction of the inner ring, providing a lubricating oil supply hole for communicating one of the cooling through holes and the opening on the inner ring raceway surface side, Rolling bearing devices that simultaneously cool and lubricate bearings have been proposed.
JP-A-6-235425 Japanese Utility Model Publication No. 6-37624

  However, in the above-mentioned Patent Document 1, the cooling through-hole has a relatively large diameter and a low flow resistance because of the need to secure a large amount of oil necessary for cooling. The lubrication hole that is branched from the middle part of the hole has a large flow resistance because the opening on the inner ring raceway surface side is narrowed by the presence of rolling elements. For this reason, there is a problem that the lubricating oil hardly flows to the oil supply hole side.

  When an annular groove is formed in the inner ring, the area is usually different between one end surface of the inner ring on the side where the annular groove is formed and the other end surface on the side where the annular groove is not formed. Assuming that both end surfaces with different areas are polished at the same time, there is insufficient polishing allowance due to polishing on the end surface on the wide area side (the end surface on the side without the annular groove). Therefore, it is necessary to re-grind the end face that is poorly polished. For this reason, there is a problem that it takes time and the processing efficiency is poor. In addition, even if it is assumed that both end faces of the inner ring are separately polished, if there is no particular means to vary the force that presses the inner ring in the axial direction during polishing of each end face, the same applies There is a problem.

  By the way, in recent years, an oil mist method and an oil-air method are frequently used as a supply form of the lubricating oil in the above-described underlace lubrication. The oil mist method is a method in which lubricating oil is sprayed, and the oil air method is a method in which a small amount of lubricating oil is ejected together with air every predetermined time. These supply systems have the advantage that lubrication can be achieved by using a relatively small amount of lubricating oil, and that there is no extra inertia load on the spindle due to the small amount of lubricating oil. However, as a result of being greatly influenced by the air flow, there is a drawback that stable lubrication cannot be performed.

That is, in the rolling bearing device, when the rolling element that is the target for jetting the lubricant passes over the opening, there is almost no gap between the opening and the rolling element, and thus the opening There is almost no air flow rate through the part, and oil mist or oil air cannot be sprayed directly onto the rolling elements, resulting in poor lubrication.
The present invention has been made in view of the above problems, and an object of the present invention is a rolling bearing device capable of smoothly supplying lubricating oil to rolling elements in under-race lubrication using an oil-air system or an oil mist system. Is to provide. Another object of the present invention is to provide a rolling bearing device capable of simplifying the polishing process for both end faces of the inner ring despite the provision of annular grooves on the end face of the inner ring.

  In order to achieve the above object, the invention according to claim 1 is a rolling bearing device forcibly lubricated by a lubricating oil that is pumped, an annular groove that is formed only on one end surface of the inner ring and stores the lubricating oil that is pumped. A plurality of oil supply holes that communicate with each of a plurality of openings formed at intervals in the circumferential direction in the vicinity of the bottom of the annular groove and in the vicinity of the inner ring raceway surface; By providing a relief portion, a clearance for lubricating oil escape is formed between the opening and the rolling element when passing over the opening, and the relief portion extends along the circumferential direction of the inner ring raceway surface. The groove is formed with one inclined surface and the other inclined surface of a groove having a V-shaped cross section, and the one inclined surface increases in diameter toward the opposite side to the inner ring raceway surface in the axial direction of the inner ring, and the other The slope of the inner ring in the axial direction of the inner ring The diameter increases toward the road surface side, the one slope faces the rolling elements and includes the opening, the other slope is adjacent to the inner ring raceway surface, and the one slope on the other slope The distance from the inner ring raceway surface is larger than the distance between the portion of the peripheral edge of the opening on the one slope and the portion closest to the other slope and the other slope. .

According to a second aspect of the present invention, in the first aspect, the diameter d of the oil supply hole and the groove depth D along the other inclined surface of the groove having the V-shaped cross section satisfy the relationship of d ≦ D ≦ 2d. It is characterized by being.
The invention according to claim 3 is characterized in that, in claim 1 or 2, the one inclined surface forms an angle of 85 ° to 95 ° with respect to a direction in which the oil supply hole extends.

According to a fourth aspect of the present invention, in the first to third aspects, the angle formed by the other slope and the axial direction of the inner ring is the same as the angle formed by the direction in which the oil supply hole extends and the axial direction of the inner ring. It is characterized by being.
According to a fifth aspect of the present invention, in any one of the first to fourth aspects, the diameter of the outer edge of the bottom portion of the annular groove is smaller than the diameter of the inner ring raceway surface, and the oil supply hole opens to the outer edge of the bottom portion. It is characterized by being.

According to a sixth aspect of the present invention, in any one of the first to fifth aspects, the annular groove is defined by a pair of inner peripheral wall surfaces opposed to each other in the radial direction of the inner ring. In addition, the diameter on the bottom side of the outer peripheral wall surface is equal to or greater than the same including the diameter on the opening edge side.
The invention according to a seventh aspect is characterized in that, in the sixth aspect, the diameter of the outer peripheral wall surface of the outer side increases as it approaches the bottom side.

According to an eighth aspect of the present invention, in any one of the first to seventh aspects, the areas of the one end surface and the other end surface of the inner ring are equal.
The invention according to claim 9 is characterized in that, in any one of claims 1 to 8, the diameter of the outer peripheral edge of the other end face of the inner ring is smaller than the diameter of the outer peripheral edge of the one end face of the inner ring. is there.
The invention according to claim 10 is the invention according to claim 9, wherein a chamfered portion is formed between the other end surface of the inner ring and the outer peripheral surface, and the diameter of the outer peripheral edge of the other end surface of the inner ring is the diameter of the outer peripheral edge of the one end surface of the inner ring. It is characterized by being smaller than.

The invention according to an eleventh aspect is characterized in that, in any one of the first to tenth aspects, the invention is used for supporting the main shaft.
In the invention according to claim 1, the lubricating oil is supplied from the bottom of the annular groove to the inner ring raceway surface through a lubricating oil supply hole, and a plurality of the oil supply holes are provided, and the openings are arranged at intervals in the circumferential direction. Therefore, a sufficient amount of lubricating oil can be supplied uniformly over the entire circumference of the inner ring raceway surface.

In addition, since a clearance for lubricating oil escape is formed between the opening portion of the oil supply hole and the rolling element by the escape portion, the air circulation amount through the opening portion can be secured stably, so that a stable amount of Lubricating oil can be fed toward the rolling elements. In particular, since the oil mist can be directly blown onto the rolling elements that pass over the opening, the lubricating effect is very high.
Further, since the relief portion is provided by forming a groove along the circumferential direction of the inner ring raceway surface, the relief portion can be easily processed.

In the invention according to claim 3, the oil supply hole directed to the rolling element is substantially perpendicular to one slope of the groove having a V-shaped cross section (specifically, a range of 85 ° to 95 °) Lubricating oil can be sprayed toward the rolling elements with good directivity. Moreover, if it is substantially right-angled, it is easy to drill the oil supply hole on the one slope.
The invention according to claim 6 has the following advantages. That is, when the diameter on the bottom side of the inner peripheral wall on the outer side of the annular groove is larger than the diameter on the opening edge side, the lubricating oil stored in the annular groove receives the centrifugal force accompanying the rotation of the inner ring, and the annular groove The inner ring moves outward in the radial direction, and is smoothly supplied to the inner ring raceway surface through an oil supply hole that communicates the outer edge of the bottom portion of the annular groove and the inner ring raceway surface. Further, even when the diameter on the bottom side of the inner peripheral wall on the outer side of the annular groove is equal to the diameter on the opening edge side, the lubricating oil that has received centrifugal force in the annular groove and has reached the outer peripheral wall surface is on the opening edge side. Rather, it tends to be urged to the bottom side of the annular groove where the oil supply hole is provided by the supply pressure of the lubricating oil into the annular groove. It can be supplied smoothly.

Hereinafter, preferred embodiments of the present invention will be described taking an angular ball bearing as an example with reference to the accompanying drawings. However, the rolling bearing according to the present invention is not limited to the angular ball bearing, and can also be applied to other inner ring rotating type rolling bearings.
FIG. 2 is a sectional view of a rolling bearing device according to an embodiment of the present invention, and FIG. 1 is an enlarged view of a main part of FIG. Referring to FIG. 2, the rolling bearing device A is configured to support the main shaft 4 inside the housing 6, and the outer ring 7 of the pair of angular type rolling bearings 1, 1 whose contact angles are opposite to each other. The outer ring spacer 2 is interposed between the inner rings 5 and 5, and the inner ring spacer 3 is interposed between the inner rings 5 and 5. The preload amount is set based on the axial dimensional difference (difference width) between the inner ring 5, the inner ring spacer 3, the outer ring 7, and the outer ring spacer 2.

The pair of outer rings 7 and 7 sandwiching the outer ring spacer 2 is sandwiched by a pair of spacers 40 and 40 on both sides, and the outer ring spacer 2, the pair of outer rings 7 and 7, and the pair of spacers 40 and 40 are The step 6c formed on the inner peripheral surface 6b of the support hole 6a of the housing 6 and the holding ring 41 screwed to the opening of the support hole 6a are collectively held and fixed.
On the other hand, the pair of inner rings 5 and 5 that support the inner ring spacer 3 are sandwiched between a pair of spacers 42 and 42, and the inner ring spacer 3, the pair of inner rings 5 and 5, and the pair of spacers 41, 41 is clamped and fixed between the flange 4 a at one end of the main shaft 4 and a holding nut 43 screwed to the outer peripheral surface of the main shaft 4. It should be noted that the inner and outer ring spacers 40 are not necessarily required at both ends in the axial direction, and may be provided only at one end.

  The outer ring spacer 2 includes rolling elements 10 supported between the inner and outer rings 5 and 7 of the rolling bearings 1 and 1, nozzles 27 and 33 for supplying oil mist or oil air toward the raceway surface, and a pair of oil supply holes. The oil supply member 12 formed with 28 is also used. Reference numeral 44 denotes an oil supply hole that is formed in a pair in the housing 6 and communicates with the oil supply holes 28, 28. 45 and 46 are oil discharge holes formed in the spacer 40 and the housing 6, respectively. Air containing lubricating oil discharged from a pump (not shown) is injected from the one end side into the bearing 1 through the oil supply hole 44 and the oil supply hole 28 through the nozzles 27 and 33, and then the oil discharge hole from the other end side. For example, the oil is returned to the lubricating oil tank or the like via the oil drain hole 45 and the oil drain hole 46.

  Next, referring to FIG. 1, the rolling bearing 1 includes a cage 11 for holding the rolling elements 10 at equal intervals, in addition to the inner ring 5, the outer ring 7 and the plurality of rolling elements 10 described above. The inner ring 5 is fixed to the main shaft 4 with a predetermined fitting accuracy, and the outer ring 7 is fixed to the housing 6. The rolling element 10 is made of a ceramic ball interposed between the angular inner ring raceway surface 8 of the inner ring 5 and the outer ring raceway surface 9 of the outer ring 7. Examples of the ceramic constituting the rolling element 10 include silicon nitride, silicon carbide, titania, mullite, and zirconia. A straight line a connecting the contact surface 8 a between the rolling element 10 and the inner ring raceway surface 8 and the contact surface 9 a between the rolling element 10 and the outer ring raceway surface 9 is inclined with respect to the radial direction of the inner ring 5 by an angle θ.

  The inner ring 5 includes an annular groove 14 on one end face 13 on the lubricating oil injection side. The annular groove 14 is partitioned by a pair of inner peripheral wall surfaces 15 and 16 and a bottom surface 17. The inner peripheral wall surfaces 15 and 16 are cylindrical surfaces concentric with the axis of the inner ring 5. The outer edge 22 of the bottom 18 of the annular groove 14 is located radially inward from the inner ring raceway surface 8. As the dimensions of the annular groove 14, for example, the axial depth of the annular groove 14 is about ¼ to ３ of the axial width of the inner ring 5, and the radial width of the annular groove 14 is About 1/4 of the radial thickness of the lubricating oil injection side end face 13 of the inner ring 5 is good, and in this embodiment, the groove width is around 3 mm and the groove depth is around 7 mm. This is because if the annular groove is larger than the above range, the strength of the inner ring 5 cannot be maintained, and if it is smaller than the above range, improvement in the lubricating performance cannot be expected. The bottom portion 18 refers to the bottom surface 17 and the inner peripheral wall surfaces 15 and 16 in the vicinity thereof.

  The inner ring 5 is formed with a chamfered portion 32 at the outer peripheral edge portion on the other end surface 31 side, thereby reducing the area of the other end surface 31, the area of the other end surface 31 and the side where the annular groove 14 is provided. The area of the one end face 13 is made equal to each other. Referring to FIG. 3, in the rolling bearing 1 made of an angular ball bearing, the rolling element 10 and the inner ring raceway surface 8 are in contact with each other only by the contact surface 8a. The inner ring raceway surface 8 is formed so as to be offset toward one side in the axial direction of the inner ring 5. A groove 20 having a V-shaped cross section (hereinafter simply referred to as a V groove 20) is formed along a peripheral edge portion 19 on the side opposite to the side where the inner ring raceway surface 8 is offset. The V groove 20 is provided to avoid the contact surface 8a on the inner ring raceway surface 8.

  The V-groove 20 is defined by a first slope 20 a facing the rolling element 10 and a second slope 20 b connected to the peripheral edge 19 of the inner ring raceway surface 8. The 1st slope 20a comprises the escape part for providing the clearance gap S between the rolling elements 10 which opposes. Openings 25 of a plurality of oil supply holes 21 through which the lubricating oil in the annular groove 14 is sent toward the rolling element 10 are formed on the first inclined surface 20a constituting the escape portion. Referring to FIG. 4, these openings 25 are arranged at equal intervals in the circumferential direction of inner ring 5. Each oil supply hole 21 has an opening 24 at the outer edge 22 of the bottom 18 of the annular groove 14.

  Referring to FIG. 3, the oil supply hole 21 is inclined with respect to the axial direction of the inner ring 5 so as to be directed to the rolling elements, and the direction in which the oil supply hole 21 extends (the direction in which the oil supply hole 21 extends) is the first. It is substantially perpendicular to the inclined surface 20a (preferable angle range is 85 ° to 95 °). Note that the groove depth D along the second inclined surface 20b, which is substantially equivalent to the gap S, satisfies the relationship of d ≦ D ≦ 2d with respect to the diameter d of the oil supply hole 21; The oil mist method and the oil jet method are preferable for achieving good lubrication. For example, when the diameter d of the oil supply hole 21 is 1 mm, the groove depth D corresponding to the amount of the gap S may be set in the range of 1 to 2 mm.

  In practice, the maximum outer diameter of the portion forming the V-groove 20 must be larger than a predetermined value in order to prevent the rolling element 10 from being pulled out (so-called counter bore needs to be secured). Therefore, the V-groove 20 cannot be formed so large, and therefore the first inclined surface 20a cannot be made too wide. Therefore, the diameter d of the oil supply hole 21 is preferably in the range of 0.5 mm to 2 mm. Further, the groove depth D corresponding to the gap amount is preferably in a range of 0.5 mm to 4 mm.

  On the other hand, the oil supply member 12 is provided with a nozzle 27 at a portion facing the opening 26 of the annular groove 14 and at a portion facing the gap between the inner peripheral surface of the outer ring 7 and the outer peripheral surface of the cage 11. A nozzle 33 is provided, and an oil supply hole 28 that communicates the nozzles 27 and 33 with an external supply source is provided. Air (oil mist or oil air) containing lubricating oil delivered from the nozzle 27 through the oil supply hole 28 is stored in the annular groove 14. Further, air containing lubricating oil is ejected from the nozzle 33 toward the outer ring raceway surface 9 side of the outer ring 7.

  Next, the lubricating operation of the rolling bearing device will be described. An air flow including lubricating oil ejected from the nozzle 27 into the annular groove 14 toward the bottom 18 is blown toward the rolling element 10 through an oil supply hole 21 opening in the bottom 18. At this time, since a clearance portion is provided by the V-groove 20 and a gap S is formed between the opening portion 25 of the oil supply hole 21 and the rolling element 10, a sufficient amount of air flow is stabilized through the gap S. Secured. With this sufficient amount of air circulation, the lubricating oil contained in the air is supplied to the rolling elements 10.

  Note that the air containing the lubricating oil also has a centrifugal force in the annular groove 14 due to the fact that it has a mass corresponding to the content of the lubricating oil. Even if the outer peripheral wall 15 is pressed against the peripheral wall 15, the outer peripheral wall 15 is made of a cylindrical surface, so that no force is generated to push air containing lubricating oil back toward the opening edge 29 of the annular groove 14. In particular, since the air containing the lubricating oil is pumped from the nozzle 24 toward the bottom 18, the air is smoothly supplied toward the bottom 18. Further, since the plurality of oil supply holes 21 opened in the inner ring raceway surface 8 are directly communicated with the bottom 18 of the annular groove 14, a sufficient amount of lubricating oil can be sent from the annular groove 14 to the inner ring raceway surface 8.

  In the present embodiment described above, a clearance S is provided between the opening 25 of the oil supply hole 21 and the rolling element 10 passing over the opening 25, so that the oil-air escape gap S is formed. In the underlace lubrication using a method, an oil mist method, or the like, the air circulation amount can be stably secured through the gap S regardless of the passage of the rolling elements 10. And since oil mist and oil air can be sprayed directly from the opening part 25 toward the rolling element 10, favorable lubrication can be achieved.

  In particular, in addition to using a plurality of lubrication dedicated oil holes 21, the openings 25 of the respective oil supply holes 21 are arranged at intervals in the circumferential direction. It becomes possible to supply uniformly over the circumference, and better lubrication can be achieved. Further, since the relief portion is provided by forming the V groove 20 along the circumferential direction of the inner ring raceway surface 8, the relief portion can be easily processed. Furthermore, since the oil supply hole 21 directed to the rolling element 10 is substantially perpendicular to the one inclined surface 20a of the V groove 20 facing the rolling element 10, the lubricating oil is sprayed toward the rolling element 10 with good directivity. Can do. Moreover, if it is substantially right angle, the oil supply hole 21 can be easily drilled in the one inclined surface 20a.

  Further, since the areas of both end faces 13 and 31 of the inner ring 5 are equal, when the both end faces 13 and 31 are simultaneously polished, the machining allowances due to the polishing process on both end faces 13 and 31 are made substantially equal. be able to. As a result, the polishing of both end faces 13 and 31 can be achieved by a single polishing process. In addition, the jig can be easily set in the subsequent process, and the re-polishing process is unnecessary as described above, so that the processing efficiency can be greatly improved and the processing time can be greatly shortened. Further, even if it is assumed that the end faces 13 and 31 are separately polished, without particularly taking measures such as changing the axial pressing force during the polishing process on the end faces 13 and 31, Each of the end faces 13 and 31 only needs to be polished once. Similarly, the processing efficiency can be improved and the processing time can be shortened.

  Further, since the annular groove 14 is formed on the end face 13 of the inner ring 5, the inner ring 5 becomes thicker than the inner ring of the conventional bearing, and as a result, the rolling element is increased by increasing the PCD (pitch circle diameter of the rolling element). There is also a secondary effect that the number can be increased and the load can be increased. In order to contribute centrifugal force, the diameter on the bottom 19 side of the outer inner peripheral wall surface 15 only needs to be equal to or larger than the diameter on the opening edge 29 side. For example, the embodiment shown in FIG. As in the form, the inner peripheral wall surface 15 outside the annular groove 14 may be a conical surface whose diameter increases as it approaches the bottom 18 side. In this case, the lubricating oil poured into the annular groove 14 receives centrifugal force and reaches the outer peripheral wall surface 15, and then the outer peripheral wall surface 15 provided with the opening 24 of the oil supply hole 21. It is urged by the centrifugal force toward the outer edge 22 side of the bottom 18.

In the present embodiment, by providing the clearance S by the escape portion, the same effect as that of the embodiment of FIG. 1 can be obtained, and the lubricating oil is supplied not only to the airflow but also to the lubricating oil supply hole 21 side by centrifugal force. Therefore, the lubricating oil can be sent to the oil supply hole 21 more smoothly, and the lubricating oil can hardly flow out from the opening 26 of the annular groove 14.
Although not shown, the inner peripheral wall surface 15 outside the annular groove 14 may be composed of a small-diameter cylindrical surface on the opening 26 side and a large-diameter cylindrical surface on the bottom 18 side. Also in this case, since the diameter on the bottom 18 side of the outer wall surface 15 on the outer side is larger than the diameter on the opening edge 29 side, the lubricating oil in the annular groove 14 is reduced as in the embodiment of FIGS. Since it is also urged | biased by the centrifugal force to the bottom 18 side along the outer peripheral wall surface 15, smooth supply of lubricating oil can be performed.

  Note that the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the scope of the present invention.

It is principal part sectional drawing of the rolling bearing apparatus concerning one Embodiment of this invention. It is a schematic sectional drawing which shows the whole rolling bearing apparatus. It is an expanded sectional view of the principal part of a rolling bearing. It is a side view of the principal part of an inner ring. It is principal part sectional drawing of the rolling bearing apparatus concerning other embodiment of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Rolling bearing, 5 ... Inner ring, 8 ... Inner ring raceway surface, 10 ... Rolling body, 13 ... One end surface, 14 ... Annular groove, 15, 16 ... Inner peripheral wall surface, 18 ... Bottom part, 20 ... V-shaped groove (section V) 20a ... first slope (one slope; relief), 20b ... second slope (other slope), 21 ... oil supply hole, 22 ... outer edge, 25 ... opening, 26 ... opening Part, 29 ... opening edge part, 31 ... other end surface, 32 ... chamfered part, S ... gap

Claims (11)

In a rolling bearing device that is forcibly lubricated by lubricating oil that is pumped,
An annular groove that is formed only on one end surface of the inner ring and stores lubricating oil to be pumped,
A plurality of oil supply holes that communicate with each of a plurality of openings formed at intervals in the circumferential direction near the bottom of the annular groove and in the vicinity of the inner ring raceway surface, and toward the rolling elements,
By providing a relief portion at the periphery of the opening, a gap for lubricating oil escape is formed between the opening and the rolling element when passing over the opening,
The relief portion is composed of one slope and the other slope of a groove having a V-shaped cross section formed along the circumferential direction of the inner ring raceway surface,
The one inclined surface is increased in diameter toward the opposite side of the inner ring raceway surface with respect to the axial direction of the inner ring, and the other inclined surface is increased in diameter toward the inner ring raceway side with respect to the axial direction of the inner ring,
The one inclined surface is opposed to the rolling element and includes the opening, and the other inclined surface is adjacent to the inner ring raceway surface,
The distance between the one slope on the other slope and the inner ring raceway surface is the peripheral edge of the opening on the one slope and the distance between the part closest to the other slope and the other slope. Rolling bearing device characterized by being large.   The diameter d of the oil supply hole and the groove depth D along the other inclined surface of the groove having the V-shaped cross section have a relationship of d ≦ D ≦ 2d. Rolling bearing device.   The rolling bearing device according to claim 1 or 2, wherein the one inclined surface forms an angle of 85 ° to 95 ° with respect to a direction in which the oil supply hole extends.   The angle formed by the other slope and the axial direction of the inner ring and the angle formed by the extending direction of the oil supply hole and the axial direction of the inner ring are the same. The rolling bearing device according to item.   5. The rolling according to claim 1, wherein a diameter of an outer edge of the bottom portion of the annular groove is smaller than a diameter of an inner ring raceway surface, and the oil supply hole opens at an outer edge of the bottom portion. Bearing device.   The annular groove is defined by a pair of inner peripheral wall surfaces facing the radial direction of the inner ring. Of these pair of inner peripheral wall surfaces, the diameter of the bottom side of the outer inner peripheral wall surface is equal to the diameter of the opening edge side. The rolling bearing device according to any one of claims 1 to 5, wherein the rolling bearing device is equal to or larger than a diameter on an opening edge side.   The rolling bearing device according to claim 6, wherein a diameter of the outer peripheral wall surface on the outer side increases as it approaches the bottom side.   The rolling bearing device according to any one of claims 1 to 7, wherein areas of the one end surface and the other end surface of the inner ring are equal to each other.   The rolling bearing device according to any one of claims 1 to 8, wherein a diameter of an outer peripheral edge of the other end surface of the inner ring is smaller than a diameter of an outer peripheral edge of the one end surface of the inner ring.   The chamfered portion is formed between the other end surface and the outer peripheral surface of the inner ring, and the diameter of the outer peripheral edge of the other end surface of the inner ring is smaller than the diameter of the outer peripheral edge of the one end surface of the inner ring. Rolling bearing device.   The rolling bearing device according to any one of claims 1 to 10, which is used for supporting a main shaft.

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