JP2008240850A - Tapered roller bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To realize a structure capable of easily performing processing of an oil passage for taking lubricant to the inside of a bearing and supplying a sufficient amount of lubricant to an inner ring raceway 4 through the oil passage. <P>SOLUTION: A plurality of through-holes 18, 18 are formed to penetrate a small diameter side collar part 9b in the axial direction composing an inner ring 5b as oil passages for taking the lubricant to the inside of a tapered roller bearing 1b. By each of the through-holes 18, 18, a sufficient amount of the lubricant can be directly supplied to the inner ring raceway 4 regardless of centrifugal force acting on the lubricant. Further, scales adhered inside each of the through-holes 18, 18 can be easily removed because diameters of each through-hole 18 can be secured large, and accordingly, the problem can be solved. <P>COPYRIGHT: (C)2009,JPO&amp;INPIT

Description

  The tapered roller bearing according to the present invention is used by being incorporated in a rotation support portion of various industrial machines, an automobile transmission, or the like.

  Roller bearings are incorporated in the rotation support parts of various industrial machines and machinery equipment. Tapered roller bearings that use tapered rollers as rolling elements are provided in the parts that constitute the rotation support parts to which large radial loads and axial loads are applied. in use. FIG. 7 shows a first example of a tapered roller bearing having a conventional structure described in Patent Document 1. In FIG. The tapered roller bearing 1 of the first example of the conventional structure includes an outer ring 3 having a conical concave outer ring raceway 2 on an inner peripheral surface, an inner ring 5 having a tapered convex inner ring raceway 4 at an intermediate portion of the outer peripheral surface, and A plurality of tapered rollers 6 are provided between the outer ring raceway 2 and the inner ring raceway 4 so as to roll freely. Each of these tapered rollers 6 has a conical convex rolling surface 7 in contact with the outer ring raceway 2 and the inner ring raceway 4 on the outer peripheral surface. In addition, among the both ends of the outer peripheral surface of the inner ring 5, a large-diameter side collar 8 is formed at the large-diameter side end, and a small-diameter side collar 9 is formed at the small-diameter side end.

  In the case of the first example of the conventional structure, a plurality of through-holes communicating the inner and outer peripheral surfaces with the axially intermediate portion of the inner ring 5 in order to take in the lubricating oil into the tapered roller bearing 1. 10 is provided. Specifically, each of these through holes 10 is formed in a portion that matches the groove portion 11 that exists in a portion that deviates from the inner ring raceway 4 to the small diameter side flange portion 9 side. As a result, each of the tapered rollers 6 rolls above the opening of each of the through holes 10 to prevent the rolling surface of each of the tapered rollers 6 from being damaged such as scratches or wear. Yes.

  The tapered roller bearing 1 configured as described above includes, for example, as shown in the drawing, the outer ring 3 is fitted and fixed to the housing 12, and the inner ring 5 is fitted and fixed to the rotary shaft 13. It is mounted between the inner peripheral surface and the outer peripheral surface of the rotary shaft 13. In such a mounted state, the radial and axial loads acting on the rotary shaft 13 can be supported by the tapered rollers 6 so that relative rotation between the rotary shaft 13 and the housing 12 is smoothly performed. Can be done.

  In the case of the first example of the conventional structure, the lubricating oil can be fed into the tapered roller bearing 1 through the oil supply hole 14 formed in the central portion of the rotating shaft 13. That is, in the case of the first example of the conventional structure, the lubricating oil fed into the oil supply hole 14 by a pump or the like (not shown) is branched from the oil supply hole 14 radially outward, and this It is possible to discharge from the groove portion 11 through each through hole 10 in which the opening on the inner diameter side communicates with the branch hole 15. In this manner, the lubricating oil fed into the tapered roller bearing 1 is used for lubrication of the rolling contact portion between the outer ring raceway 2 and the inner ring raceway 4 and the rolling surface of each tapered roller 6. .

  However, in the case of the first example of the conventional structure having the above-described structure, there arises a problem that sufficient lubrication performance cannot be obtained when a tapered roller bearing 1 is used. That is, in the case of the first example of the conventional structure, in order to prevent the rolling surface of each tapered roller 6 from being damaged such as scratches, the through hole 10 for taking in the lubricating oil is provided with the groove portion. 11 is formed in a portion that matches with 11. For this reason, when a small-sized one is used as the tapered roller bearing 1, it is necessary to reduce the diameter of each through hole 10 in accordance with the width of the groove 11. As a result, the amount of lubricating oil that can be taken into the tapered roller bearing 1 is reduced, and sufficient lubrication performance may not be obtained.

  Further, in the case of the first example of the conventional structure, the following inconvenience is caused with respect to the hole processing for forming each through hole 10. That is, if the hole processing of each through hole 10 is performed after the inner ring 5 is subjected to heat treatment such as quenching, the increase in hardness of the inner ring 5 increases the time and cost required for the hole processing. On the other hand, if the hole processing is performed before the heat treatment, a scale such as an oxide film may adhere to the formed through hole 10 and the through hole 10 may be blocked. In particular, in the case of the small-diameter through hole 10, not only the scale is easily clogged but also the operation of removing the scale becomes difficult.

  On the other hand, Patent Document 2 describes a tapered roller bearing that can solve the above-described problems. FIG. 8 shows a tapered roller bearing 1a of the second example of the conventional structure described in Patent Document 2. In the case of the tapered roller bearing 1a of the second example of this conventional structure, in order to take in the lubricating oil into the tapered roller bearing 1a, a small-diameter side end surface of the inner ring 5a (small-diameter side flange portion is provided in the axial end surface). A plurality of concave grooves 16 communicating with both the inner and outer peripheral surfaces of the inner ring 5a are formed on the left end surface of the inner ring 5a. Further, one end surface of the spacer 17 in the axial direction (the right side surface in FIG. 8) is brought into contact with the end surface on the small diameter side of the inner ring 5a in which such a concave groove 16 is formed. The opening is covered (closed).

  In the case of the tapered roller bearing 1a of the second example of the conventional structure having such a configuration, the lubricating oil fed into the oil supply hole 14 formed in the center portion of the rotating shaft 13 is supplied to the branch hole 15 and the above-mentioned Through each concave groove 16, it can be discharged into the tapered roller bearing 1a. With such a configuration, in the case of the second example of the conventional structure, each rolling contact portion between the outer ring raceway 2 and the inner ring raceway 4 and the rolling surface of each tapered roller 6 can be lubricated.

  Further, in the case of the tapered roller bearing 1a of the second example of the conventional structure, the size (opening width) of each concave groove 16 is limited even when a small one is used as the tapered roller bearing 1a. There is nothing. For this reason, it is possible to secure the amount of lubricating oil taken into the tapered roller bearing 1a. Further, as described above, since each of the concave grooves 16 is formed on the end surface on the small diameter side of the inner ring 5a, even when a scale adheres to the inner grooves 5a due to heat treatment applied to the inner ring 5a. This scale can be easily removed. Thus, according to the tapered roller bearing 1a of the second example of the conventional structure, it is possible to solve the problem that occurs in the case of the first example of the conventional structure described above.

  However, in the case of the tapered roller bearing 1a of the second example of the conventional structure, the ratio of the lubricating oil supplied to the inner ring raceway 4 portion of the lubricating oil that has passed through each of the concave grooves 16 is reduced. Problems arise. That is, in the case of the second example of the conventional structure, the lubricating oil fed into the oil supply hole 14 is discharged through the concave grooves 16 outward in the radial direction of the end surface on the small diameter side of the inner ring 5a. become. For this reason, in order to feed this lubricating oil toward the inner ring raceway 4, it is necessary to ride over (straddle) a part of the small-diameter side flange 9a. Therefore, the small diameter side flange 9a serves as a so-called weir, and the amount of lubricating oil that can reach the inner ring raceway 4 is reduced.

  Further, during operation of a tapered roller bearing, it is known that the lubricating oil moves radially outward within the bearing by the action of centrifugal force as shown by the arrow in FIG. 9 (see Patent Document 3). For this reason, the amount of lubricating oil that can reach the inner ring raceway 4 that exists radially inward of the small diameter side flange 9a out of the lubricating oil supplied from the outside in the radial direction of the small diameter side flange 9a is limited. Amount. As described above, in the case of the tapered roller bearing 1a of the second example of the conventional structure described above, since there is a lack of lubricating oil capable of lubricating the inner ring raceway 4, the inner ring raceway 4 and the rolling surface of each tapered roller 6 are There is a possibility of causing problems such as wear and temperature rise at the rolling contact portion. In particular, such a problem is caused when the tapered roller bearing 1a is incorporated in a planetary gear device that constitutes an automatic transmission or the like that rotates (revolves) the tapered roller bearing 1a itself or a rotation support portion that rotates at high speed. In addition, the centrifugal force acting on the lubricating oil increases and becomes prominent.

Japanese Utility Model Publication No. 56-157428 JP 2005-291445 A Japanese Utility Model Publication No. 58-150620

  The present invention can easily process the oil passage for taking the lubricating oil into the bearing and can realize a structure capable of supplying a sufficient amount of the lubricating oil to the inner ring raceway through the oil passage. It is a thing.

The tapered roller bearing of the present invention is similar to the previously known tapered roller bearing, and has an outer ring having a tapered outer ring raceway on the inner peripheral surface, and a tapered convex surface in the middle of the outer peripheral surface. An inner ring raceway is provided between the inner ring having a large diameter side flange at the large diameter end and a small diameter flange at the small diameter end, and between the outer ring raceway and the inner ring raceway so as to roll freely. A plurality of tapered rollers are provided.
In particular, in the tapered roller bearing of the present invention, an oil passage that communicates (penetrates) both side surfaces of the small diameter side flange is provided in the small diameter side flange.

When the tapered roller bearing described in claim 1 as described above is implemented, as described in claim 2, the oil passage is formed in a radial intermediate portion or an inner end portion of the small-diameter side flange portion. Through holes.
Alternatively, as described in claim 3, the oil passage is a concave groove (notch) opened on the outer peripheral edge side of the small-diameter side flange.

Further, when the tapered roller bearing according to any one of claims 1 to 3 as described above is implemented, preferably, as described in claim 4, an oil guide for feeding lubricating oil into the oil passage. A groove is formed in the radial direction from the inner peripheral edge of the small-diameter side end surface on the small-diameter side end surface of the inner ring.
Also, regardless of whether or not the oil guide groove is formed on the small-diameter end face of the inner ring, for example, the axial end face of another annular member (for example, a spacer) is brought into contact with the small-diameter end face of the inner ring. Can be used. In this case, when the oil guide groove is not formed on the small-diameter side end face of the inner ring, the axial direction of the separate member is used to feed the lubricating oil into the oil passage formed in the small-diameter side flange of the inner ring. Oil guide grooves formed on the end face can be used. In this case, a radially long concave groove is formed as an oil guide groove on the axial end surface of the separate member, and the small diameter side end surface of the inner ring is in contact with the axial end surface of the separate member. Thus, the concave groove communicates with the oil passage.

In the case of the tapered roller bearing of the present invention configured as described above, a sufficient amount of lubricating oil can be supplied to the inner ring raceway through an oil passage that communicates both side surfaces of the small-diameter side flange. That is, in the case of the present invention, the lubricating oil is directly fed toward the inner ring raceway through the oil passage formed at a position closer to the inner ring raceway, not from the radially outer side of the small diameter side flange portion. Can do. Therefore, a sufficient amount of lubricating oil can be supplied to the inner ring raceway.
Further, in the case of the present invention, the degree of freedom of design regarding the size (cross-sectional area) and shape (cross-sectional shape) of the oil passage is high, and the size of the oil passage is also large in the case of a small tapered roller bearing. A sufficient thickness (cross-sectional area) can be secured. For this reason, even when a scale adheres in the oil passage due to the heat treatment applied to the inner ring, the scale can be easily removed. Further, when the oil passage is formed after the heat treatment, it can be easily processed by using, for example, electric discharge machining. Thus, in the case of this invention, the processing operation of the oil passage for taking in lubricating oil inside a tapered roller bearing can be made easy.

[First example of embodiment]
1 and 2 show a first example of an embodiment of the present invention corresponding to claims 1 and 2. The feature of this example is that a plurality of through-holes 18 that penetrate the small-diameter side flange 9b in the axial direction are formed in the small-diameter flange 9b constituting the inner ring 5b in order to take in the lubricating oil into the tapered roller bearing 1b. 18 is formed. Since the structure and operation of the other parts are almost the same as those of the conventional structure described above, the explanation for the equivalent parts will be omitted or simplified, and the following will focus on the characteristic parts of this example.

  In the case of this example, as shown in FIG. 2, a total of eight through holes 18, 18 are formed at equal intervals in the circumferential direction in the radially inward portion of the small-diameter side flange 9b. The diameter dimension of each of these through-holes 18 and 18 is about ½ of the width dimension in the radial direction of the small-diameter side flange portion 9b, and the respective central axes are arranged substantially parallel to the generatrix of the inner ring raceway 4. ing. A portion of the opening edge of each of the through holes 18 and 18 opened on the inner side surface of the small-diameter side flange portion 9b is located on the radially inner side of the inner ring 5b, adjacent to the inner ring raceway 4. The bottom of the groove 11 is continuous.

  In the case of this example, the through-holes 18 and 18 as described above are processed by cutting using a tool such as a drill before the inner ring 5b is subjected to heat treatment such as quenching and tempering. For this reason, a scale such as an oxide film adheres to the inner peripheral surface of each of the through holes 18 and 18 by the heat treatment performed thereafter. In the case of this example, this scale is placed in the through holes 18 and 18. A polishing tool such as a flap wheel is inserted and removed.

  In the case of this example, in order to introduce the lubricating oil to the through holes 18, 18, one end surface in the axial direction of the spacer 17 a is brought into contact with the end surface on the small diameter side of the inner ring 5 b. A total of eight oil guide grooves 19 are provided on the one end face in the axial direction of the spacer 17a from the inner peripheral edge of the one end face in the radial direction to the intermediate portion in the radial direction. These oil guide grooves 19 are arranged at equal intervals in the circumferential direction, and the respective opening widths are the same as the diameter dimensions of the respective through holes 18, 18. For this reason, in the case of this example, when the axial end surface of the spacer 17a and the small-diameter side end surface of the inner ring 5b are brought into contact with each other, the oil guide grooves 19 and the through holes 18, 18 These oil guide grooves 19 and the respective through holes 18 and 18 are communicated with each other by matching the phases of each other. Further, in this state, among these oil guide grooves 19, the opening on the inner peripheral edge side of the spacer 17 a is communicated with the opening of the branch hole 15 formed on the outer peripheral surface of the rotating shaft 13.

  In the case of this example having the above-described configuration, the lubricating oil fed into the oil supply hole 14 formed in the central portion of the rotating shaft 13 passes through the branch hole 15 and the oil guide grooves 19 to It can feed into each through-hole 18,18. The lubricating oil fed into each of the through holes 18, 18 can be discharged toward the groove 11 provided adjacent to the inner ring raceway 4. In this way, in the case of this example, the lubricating oil can be directly fed toward the inner ring raceway 4 without straddling the radially outer side of the small-diameter side flange 9b. For this reason, the amount of lubricating oil that can be supplied to the inner ring raceway 4 can be increased. Particularly in the case of this example, the lubricating oil passing through each of the through holes 18 and 18 does not move (scatter) radially outward due to the action of centrifugal force. It can be supplied to the inner ring raceway 4.

  In the case of this example, since the lubricating oil can be fed toward the inner ring raceway 4 from a total of eight through-holes 18, 18, the lubricating oil is almost evenly distributed on the peripheral surface of the inner ring raceway 4. Can be supplied. In the case of this example, each through hole 18, 18 is ensured to have a diameter dimension that is approximately ½ of the width dimension in the radial direction of the small diameter side flange 9 b. The amount of lubricating oil that can pass through 18 is increased.

As described above, in the case of this example, since it is possible to prevent the inner ring raceway 4 from being deficient in lubricating oil, the rolling contact portion between the inner ring raceway 4 and the rolling surface of each tapered roller 6 is subjected to wear and tear. It is possible to effectively prevent problems such as abnormal heat generation. For this reason, even when the tapered roller bearing 1b of this example is incorporated into a rotating support portion that rotates at a high speed or a planetary gear device that revolves the tapered roller bearing 1b itself, a lack of lubricating oil becomes a problem. There is nothing, and it can be preferably used for such applications.
For the outer ring raceway 2, a part of the lubricating oil discharged from each of the through holes 18, 18 is supplied by moving outward in the radial direction by the action of centrifugal force, and each of the tapered rollers. 6 is supplied via the rolling contact surface 6, so that there is no problem of lack of lubricating oil.

  In the case of this example, as described above, since the diameter of each of the through holes 18, 18 is large, the scale is removed, and a polishing tool is inserted into each of the through holes 18, 18. Can be done. Therefore, the scale removal operation can be easily performed. In order to remove the scale, it is possible to use a cleaning liquid in addition to the polishing tool, but it is preferable to use the polishing tool from the viewpoint of reducing the working time. Further, if the through holes 18 and 18 are formed by, for example, electric discharge machining after the inner ring 5b is heat-treated, the above-described scale removal work can be omitted.

[Second Example of Embodiment]
3 and 4 show a second example of an embodiment of the present invention corresponding to claims 1 and 3. The feature of this example is that a plurality of concave grooves 20 and 20 are formed in a state of opening to the outer peripheral edge side of the small-diameter side flange portion 9c in order to take lubricating oil into the tapered roller bearing 1b. The structure and operation of the other parts are substantially the same as those of the first example of the embodiment described above and the conventional structure described above. For this reason, the explanation about the equivalent part is omitted or simplified, and hereinafter, the explanation will focus on the characteristic part of this example.

  In the case of this example, as shown in FIG. 4, a total of four concave grooves 20, 20 are formed at equal intervals in the circumferential direction in a state where they are opened on the outer peripheral edge side of the small-diameter side flange 9 c. . Each of the concave grooves 20, 20 has a circular arc cross section, and each has a radius of curvature that is substantially the same as the width of the small diameter side flange 9c in the radial direction. Further, the bottom of each of the concave grooves 20, 20 is continued to the bottom of the groove 11 provided adjacent to the inner ring raceway 4.

  Also in the case of this example, the spacer 17b in which the oil guide groove 19a is formed on one end face in the axial direction is brought into contact with the end face on the small diameter side of the inner ring 5c. However, in this example, a spacer provided with a total of four oil guide grooves 19a is used as the spacer 17b. The opening width of each oil guide groove 19a is the same as the opening width (width dimension in the circumferential direction) of each of the concave grooves 20, 20. And in the state which contacted the axial direction one end surface of the said spacer 17b, and the small diameter side end surface of the said inner ring | wheel 5c, the phase of each said oil guide groove 19a and each said concave groove 20, 20 was match | combined, and these Each oil guide groove 19a and each concave groove 20, 20 are communicated with each other.

  Also in the case of this example having the above-described configuration, the lubricating oil fed into the oil supply hole 14 formed in the central portion of the rotating shaft 13 is passed through the branch hole 15 and the oil guide grooves 19a. Each groove 20 can be fed into the groove 20. Then, the lubricating oil fed into the concave grooves 20 and 20 can be discharged toward the groove portion 11 provided adjacent to the inner ring raceway 4. Thus, also in the case of this example, the lubricating oil can be directly fed toward the inner ring raceway 4 without straddling the radially outer side of the small diameter side flange 9c. For this reason, the amount of lubricating oil that can be supplied to the inner ring raceway 4 can be increased.

In the case of this example, the oil passages for taking the lubricating oil into the tapered roller bearing 1b are the recessed grooves 20 and 20 opened on the outer peripheral side of the small diameter side flange 9c. Lubricating oil passing through the concave grooves 20 and 20 is likely to be scattered outward in the radial direction by the action of centrifugal force. For this reason, in the case of this example, in order to ensure the amount of lubricating oil that can be supplied to the inner ring raceway 4, the cross-sectional area of each of the concave grooves 20, 20 is set to each through hole 18 in the case of the first example. , 18 is secured to increase the amount of lubricating oil that can pass through each of the concave grooves 20, 20. In this example, the amount of lubricating oil that can be supplied to the outer ring raceway 2 can be increased by such a configuration. Furthermore, in the case of this example, since each said recessed groove 20, 20 is provided in the state opened to the outer peripheral edge side of the said small diameter side collar part 9c, each said recessed groove 20, 20 is heat-processed to the inner ring | wheel 5c. Even if the scale adheres to the inside, the scale can be easily removed.
Other configurations and operations are the same as those in the first example of the embodiment described above.

[Third example of embodiment]
5 and 6 show a third example of an embodiment of the present invention corresponding to claims 1, 2, and 4. FIG. The feature of this example is that a plurality of through holes 18 and 18 are formed in the small-diameter side flange portion 9d in order to take in the lubricating oil into the tapered roller bearing 1b, and the lubricating oil is fed into these through holes 18 and 18. This is because the oil guide grooves 19b, 19b are formed on the end surface on the small diameter side of the inner ring 5d. The structure and operation of other parts are substantially the same as those of the first example of the embodiment described above and the conventional structure described above. For this reason, the explanation about the equivalent part is omitted or simplified, and hereinafter, the explanation will focus on the characteristic part of this example.

  Also in the case of this example, similarly to the first example of the above-described embodiment, eight small through holes 18 and 18 that penetrate the small diameter side flange 9d in the axial direction are formed in the small diameter side flange 9d. is doing. In particular, in the case of this example, in order to feed the lubricating oil into these through holes 18, 18, oil guide grooves 19 b, 19 b are formed on the end surface on the small diameter side of the inner ring 5 d. Specifically, the oil guide grooves 19b and 19b are formed on the small diameter side end surface of the inner ring 5d from the inner periphery of the small diameter side end surface to the intermediate portion in the radial direction, and the oil guide grooves 19b and 19b. The outer diameter side portion is communicated with each of the through holes 18 and 18. Further, the opening widths of the oil guide grooves 19b and 19b are substantially the same as the diameters of the through holes 18 and 18, respectively.

  Also in this example, one end surface in the axial direction of the spacer 17 is brought into contact with the end surface on the small diameter side of the inner ring 5d. However, in the case of this example, the oil guide grooves 19b, 19b are directly formed on the end surface on the small diameter side of the inner ring 5d, so that the one end surface in the axial direction of the spacer 17 is simply a flat surface. The upper openings of the oil guiding grooves 19b and 19b are covered.

  In the case of this example having the above-described configuration, the lubricating oil fed into the oil supply hole 14 formed at the center of the rotating shaft 13 is passed through the branch hole 15 and the oil guide grooves 19b and 19b. , Can be fed into the through holes 18, 18. Therefore, also in this example, the lubricating oil can be directly fed toward the inner ring raceway 4 without straddling the radially outer side of the small-diameter side flange 9d. For this reason, the amount of lubricating oil that can be supplied to the inner ring raceway 4 can be increased.

Particularly in the case of this example, the oil guide grooves 19b, 19b for feeding the lubricating oil to the respective through holes 18, 18 are directly formed on the end surface on the small diameter side of the inner ring 5d. In addition, it is possible to use a flat one end surface in the axial direction. Accordingly, as in the first and second examples of the above-described embodiment, each oil guide groove 19 (19a) formed in the spacer 17a (17b) and each through hole 18 (or each recess) are formed. The operation of matching the phase with the groove 20) becomes unnecessary. Therefore, the work of assembling the tapered roller bearing 1b and the spacer 17 with respect to the rotating shaft 13 can be facilitated.
Other configurations and operations are the same as those in the first example of the embodiment described above.

  The shape, number, radial position, etc. of the through holes (and concave grooves) corresponding to the oil passages described in the claims are the structures described in the first to third examples of the embodiment described above. However, the design can be determined in accordance with the dimensions of the tapered roller bearing, the intended use, the intended purpose, and the like. Moreover, the structures from the first example to the third example of the embodiment described above can also be implemented in combination.

The fragmentary sectional view which shows the use condition of the tapered roller bearing of the 1st example of embodiment of this invention. The front view of the small diameter side end surface of an inner ring | wheel similarly. The figure similar to FIG. 1 which shows the 2nd example of embodiment of this invention. The same figure as FIG. The figure similar to FIG. 1 which shows the 3rd example of embodiment of this invention. The same figure as FIG. The fragmentary sectional view which shows the use condition of the tapered roller bearing of the 1st example of conventional structure. The fragmentary sectional view which shows the use condition of the tapered roller bearing of the 2nd example of conventional structure. The fragmentary sectional view of a tapered roller bearing shown in order to demonstrate that lubricating oil moves to the diameter direction outside at the time of operation.

Explanation of symbols

1, 1a, 1b Tapered roller bearing 2 Outer ring raceway 3 Outer ring 4 Inner ring raceway 5, 5a, 5b, 5c, 5d Inner ring 6 Tapered roller 7 Rolling surface 8 Large diameter side flange 9, 9a, 9b, 9c, 9d Small diameter side Gutter part 10 Through hole 11 Groove part 12 Housing 13 Rotating shaft 14 Oil supply hole 15 Branching hole 16 Groove hole 17, 17a, 17b Spacer 18 Through hole 19, 19a, 19b Oil guide groove 20 Groove groove

Claims (4)

  An outer ring having a conical concave outer ring raceway on the inner peripheral surface, a conical convex inner ring raceway in the middle of the outer peripheral surface, a large diameter side collar on the large diameter side end, and a small diameter on the small diameter side end In a tapered roller bearing comprising an inner ring having side flanges and a plurality of tapered rollers provided between the outer ring raceway and the inner ring raceway so as to be freely rollable, A tapered roller bearing characterized in that an oil passage is provided to communicate both side surfaces of the small-diameter side flange.   The tapered roller bearing according to claim 1, wherein the oil passage is a through hole formed in a radially intermediate portion or an inner end portion of the small-diameter side flange portion.   The tapered roller bearing according to claim 1, wherein the oil passage is a concave groove opened on an outer peripheral edge side of the small-diameter side flange portion.   The oil guiding groove for feeding the lubricating oil into the oil passage is formed in the radial direction from the inner peripheral edge of the small diameter side end surface on the small diameter side end surface of the inner ring. The tapered roller bearing described.

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