JP2011226571A - Tapered roller bearing - Google Patents

Abstract

PROBLEM TO BE SOLVED: To achieve a structure which improves durability in a lubrication failure condition, that is, enables sufficient extension of time taken to make rotation impossible by seizing.SOLUTION: Of a large-diameter-side rim part 12a making up a holder 5d, the inner circumferential surface of each part matching each pocket 15a in circumferential phase is provided with an oil-retaining recession 19 recessed outwardly in the radial direction. A part of the bottom of each oil-retaining recession 19 that is open to the inner surface of each pocket 15a is set opposite to a recession 20 formed on a large-diameter-side end face 10 of each tapered roller 4a held in each pocket 15a. When lubrication fails, a lubricating oil remaining in each oil-retaining recession 19 is used effectively to lubricate a sliding part between the large-diameter-side end face 10 and an axial inside face 11 of a large-diameter-side collar 8.

Description

  The present invention supports various rotating shafts that rotate in a state where a large radial load and thrust load are applied, such as a transmission shaft that constitutes an axle of a railway vehicle and a drive shaft, or a pinion shaft that constitutes a differential gear for an automobile. The present invention relates to improvement of tapered roller bearings. Specifically, by improving the shape and structure of the cage that holds a plurality of tapered rollers constituting a tapered roller bearing in a freely rolling manner, the durability in a poorly lubricated state is improved, that is, in a poorly lubricated state. It is intended to extend the time until the rotation becomes impossible due to seizure.

  For example, a tapered roller bearing 1 as shown in FIG. 10 is incorporated in a rotation support portion for a rotating shaft that rotates while supporting a large radial load and thrust load, such as a pinion shaft of a differential gear. The tapered roller bearing 1 includes an outer ring 2 and an inner ring 3 that are arranged concentrically with each other, a plurality of tapered rollers 4 and 4, and a cage 5. Out of these, the outer ring 2 has a concave outer ring raceway 6 on the inner peripheral surface. The inner ring 3 is arranged on the inner diameter side of the outer ring, and has a partially conical convex inner ring raceway 7 on the outer peripheral surface. Further, a large-diameter side collar 8 is formed at the large-diameter end of the outer peripheral surface of the inner ring 3, and a small-diameter collar 9 is formed at the small-diameter end, respectively. It is formed in a protruding state. The tapered rollers 4, 4 are arranged so as to roll freely between the outer ring raceway 6 and the inner ring raceway 7, and the large-diameter side end surfaces (heads) 10 are respectively connected to the large ring ends 4. It is made to oppose with the axial inner surface 11 of the diameter side collar part 8. FIG. The cage 5 is for holding the tapered rollers 4 and 4.

  The cage 5 is arranged concentrically and spaced apart in the axial direction, and has a large-diameter side rim portion 12 and a small-diameter side rim portion 13 each having an annular shape, and both the rim portions 12, 13. A plurality of pillars 14 and 14 are provided between the two. And in order to hold | maintain each said tapered roller 4 and 4 so that rolling is possible, respectively, the part enclosed by these two rim | limb parts 12 and 13 and a pair of pillar parts 14 and 14 which adjoin each other in the circumferential direction. Pockets 15 and 15. Note that the cage 5 shown in FIG. 10 is formed by bending a metal plate, and by forming a bent plate portion 16 having an inward flange shape that is bent radially inward from the end portion on the small diameter side, The overall rigidity is secured.

  11 to 13 show a tapered roller bearing 1 incorporating a cage 5a having a different shape as a second example of a conventionally known tapered roller bearing. The cage 5a is integrally formed by injection molding a synthetic resin or by machining a metal material. The basic structure is the same as the cage 5 incorporated in the first example of the conventional structure shown in FIG. 10 described above. Part 12a and a small-diameter side rim part 13a and a plurality of pillar parts 14a, 14a, and the four rims are surrounded by a pair of pillar parts 14a, 14a adjacent to each other in the circumferential direction. The portions are pockets 15a and 15a, respectively. In the case of this example, since both the rim portions 12a and 13a themselves can sufficiently secure rigidity, the bent plate portion (see FIG. 10) like the cage 5 of the first example is not provided. A circular recess 20 is provided at the center of the large-diameter end face 10 of the tapered roller 4a.

  In any structure, when the tapered roller bearing 1 is operated, each of the tapered rollers 4 and 4a is caused by a large radial load applied from the partially tapered concave outer ring raceway 6 and the partially tapered convex inner ring raceway 7. It tends to be displaced to the larger diameter side of the tracks 6 and 7. As a result, during operation of the tapered roller bearing 1, the tapered rollers 4, 4 a are brought into contact with the large-diameter side end face 10 and the large-diameter side flange 8 with the relative rotation of the outer ring 2 and the inner ring 3. It rotates and revolves while making sliding contact with the axially inner side surface 11. In this case, the frictional state between the large-diameter side end face 10 and the axially inner side surface 11 of the large-diameter side flange 8 is almost sliding friction, so that wear resistance and seizure resistance are ensured. From the aspect of doing, it becomes very severe conditions. For this reason, conventionally, sufficient lubricating oil is supplied to the rotation support portion in which the tapered roller bearing 1 as described above is incorporated, so that the axially inner side surface 11 of the large-diameter side end surface 10 and the large-diameter side flange portion 8 is supplied. A sufficient lubricating oil film is interposed on the sliding surface.

  In the normal state in which a sufficient amount of lubricating oil can be supplied to the rotation support portion in which the tapered roller bearing 1 is incorporated, the tapered roller bearing 1 having the conventional structure as described above does not cause any particular problem. However, regardless of the type of the rotation support device in which the tapered roller bearing 1 is incorporated, the possibility that the lubricating oil supplied to the tapered roller bearing 1 is insufficient or depleted due to some failure or poor maintenance is completely eliminated. You can't deny it. When the lubricating oil supplied to the tapered roller bearing 1 is insufficient or exhausted, the sliding surface between the large-diameter side end face 10 and the axially inner side face 11 of the large-diameter side flange 8 is the most severe condition. The wear of the steel progresses remarkably. In a further remarkable case, the large-diameter side end face 10 and the axially inner side face 11 are adhered to each other, so that the tapered rollers 4 and 4a cannot be rotated and revolved. Further, the tapered rollers 4 and 4a The rolling contact surface and the outer ring raceway 6 adhere to each other, and so-called seizure is generated in which relative rotation between the outer ring 2 and the inner ring 3 becomes impossible.

  If such burn-in occurs, it becomes difficult to move the vehicle (railway vehicle or automobile) as well as normal operation of the vehicle, and problems such as delay in restoration of the railroad or traffic congestion are likely to occur. In addition, the inability to rotate the rotation support part causes a failure of other parts, and problems such as cost and time required for repair are likely to occur. In view of such circumstances, in Patent Documents 1 and 2, a sliding contact portion between the large-diameter side end surface of each tapered roller and the axially inner side surface of the large-diameter side flange is provided in Patent Documents 1 and 2 effectively. The structure to be lubricated is described. 14 to 16 show two examples of the conventional structure described in Patent Document 1 among them.

  First, in the case of the first example of the known countermeasure structure shown in FIG. 14, this is done by bending the large-diameter side end of the metal plate cage 5 b inward in the radial direction. An oil retaining portion 17 is provided over the entire circumference at the end on the large diameter side of the inner peripheral surface of the cage 5b. In the first example of this conventional structure, the lubricating oil stored in the oil retaining portion 17 is applied to the sliding contact portion between the large-diameter side end surface 10 of the tapered roller 4 and the axially inner side surface 11 of the large-diameter side flange portion 8. It is intended to suppress wear during poor lubrication.

  Next, in the case of the second example of the known countermeasure structure shown in FIGS. 15 to 16, the cage 5c is bent outwardly in the small diameter side by bending the cage 5c toward the outside in the radial direction. An oil retaining portion 17a is provided at the end on the small diameter side of the outer peripheral surface of 5c. In addition, the oil retaining portion 17a is divided into a plurality of parts in the circumferential direction by the partition plates 18 and 18. The second example of this conventional structure prevents the lubricating oil from adhering to the outer peripheral surface of the cage 5c and reaching the small diameter end of the cage 5c. This is supplied to the sliding contact portion between the radial side end surface 10 and the axially inner side surface 11 of the large diameter side flange 8 so as to suppress wear during poor lubrication.

  In the case of two examples of conventionally known countermeasured structures as described above, a small amount of lubricating oil can be obtained even though excellent durability can be obtained as compared with the unmeasured structures shown in FIGS. Cannot be efficiently supplied to the sliding contact portion between the large-diameter side end face 10 and the axially inner side face 11 (a small amount of lubricating oil can be effectively used). First, in the case of the structure of the first example shown in FIG. 14, the amount of lubricating oil that does not adhere to the large-diameter end face 10 of each tapered roller 4 while remaining in the oil retaining portion 17 increases. It is difficult to effectively use a small amount of lubricating oil. Further, the structure of the second example shown in FIGS. 15 to 16 is provided in a portion where the oil retaining portion 17a is largely separated from the sliding contact portion between the large-diameter side end surface 10 and the axial inner side surface 11, It is difficult to effectively use a small amount of lubricating oil for lubricating the sliding contact portion. Thus, the fact that a small amount of lubricating oil cannot be effectively used for lubrication of the sliding contact portion between the large-diameter side end face 10 and the axially inner side face 11 is shown in FIG. Even if the oil retaining portion 17 is provided with the partition plate portions 18 and 18 shown in FIG.

  In Patent Document 2, the lubricating oil guided along the inner peripheral surface of the cage is connected to the large-diameter side end surface of the tapered roller by an inward large-diameter side flange provided at the large-diameter side edge of the cage. A structure is described that leads to a sliding contact portion with the inner surface in the axial direction of the large-diameter side flange on the outer peripheral surface of the inner ring. In the case of the third example of the countermeasured structure described in Patent Document 2 as described above, a small amount of lubricating oil is applied to the large-diameter side end face even if superior durability can be obtained compared to the non-measured structure. There is room for improvement in terms of the surface that is efficiently supplied by the sliding contact portion between the inner surface and the axially inner surface.

JP 2007-40512 A JP 2007-270851 A

  In view of the circumstances as described above, the present invention has a structure capable of sufficiently improving the durability in a poorly lubricated state, that is, extending the time until it becomes non-rotatable due to seizure after being in a poorly lubricated state. It was invented to realize.

The tapered roller bearing of the present invention includes an outer ring, an inner ring, a plurality of tapered rollers, and a cage, like the conventionally known tapered roller bearing.
Among these, the outer ring has a partially conical concave outer ring raceway on the inner peripheral surface.
Further, the inner ring is disposed concentrically with the outer ring on the inner diameter side of the outer ring. On the outer peripheral surface, a partially conical convex inner ring raceway, and a radial direction from a large diameter side end of the inner ring raceway. It has a large-diameter side flange projecting outward.
Further, each of the tapered rollers is disposed between the inner ring raceway and the outer ring raceway so as to be able to roll, and each large diameter side end face is opposed to the axial side surface of the large diameter side flange. .
The cage is for holding the tapered rollers.
The retainer is arranged concentrically and spaced apart in the axial direction, each having a ring-shaped large-diameter side rim portion and small-diameter side rim portion, and between these rim portions. And a plurality of pillars spanned. And it has the structure which used as the pocket for hold | maintaining each said tapered roller, respectively the part enclosed by the circumference | surroundings by these both rim | limb parts and a pair of pillar parts adjacent to the circumference direction.

  Preferably, the above-described structure is a tapered roller having a tangent line formed by bringing the raceway surface of the outer ring and the rolling surface of the roller into contact with each other, and an angle (contact angle) formed by a rotating shaft of the bearing of 20 ° or more. Used for bearings.

  In particular, in the tapered roller bearing of the present invention, in the large-diameter side rim portion, the phase in the circumferential direction is at least on the inner peripheral surface portion of the portion that matches with some of the pockets. An oil retaining recess that is recessed radially outward is provided.

  And the part opened to the inner surface of the said pocket among the bottom surfaces of this oil retaining recessed part is made to oppose the recessed part formed in the large diameter side end surface of the tapered roller hold | maintained in the said pocket.

  When implementing such a tapered roller bearing of the present invention, preferably, the number of the oil retaining recesses is the same as the number of the pockets as in the invention described in claim 2. And each of these oil retaining recesses provided in an independent state with respect to the circumferential direction is opened toward each of the pockets.

  Further, preferably, as in the invention described in claim 3, the bottom portion of the oil retaining recess is inclined in a direction toward the radially outward direction toward the pocket.

  More preferably, as in the invention described in claim 4, the inner peripheral surface of the large-diameter side rim portion is inclined in a direction toward the radially outward direction toward the pocket.

The tapered roller bearing of the present invention configured as described above improves the durability in a poorly lubricated state by acting as follows, i.e., from the poorly lubricated state until it becomes non-rotatable due to seizure. The time can be extended more fully.
As in the case of general tapered roller bearings, the lubricating oil during operation of the rotary machine device incorporating the tapered roller bearing of the present invention is a pump based on the centrifugal force associated with the revolving motion of each tapered roller. By the action, the bearing inner space between the inner peripheral surface of the outer ring and the outer peripheral surface of the inner ring flows from the small diameter side to the large diameter side of the outer ring raceway and the inner ring raceway. When the supply amount of the lubricating oil is sufficient, the lubricating oil flowing through the bearing inner space in this way is connected to the large-diameter side end surface of each tapered roller and the axial inner surface of the large-diameter side flange of the inner ring outer peripheral surface. Also fully lubricate the sliding contact area. Further, in this state, a part of the lubricating oil flowing in the bearing inner space flows into the oil retaining recess formed on the inner peripheral surface of the large-diameter side rim portion while flowing from the opening on each pocket side. It is discharged to the outer edge side in the axial direction of the radial rim portion. In other words, the lubricating oil that has previously entered the oil retaining recess is pushed out of the oil retaining recess by the lubricating oil that newly flows from the opening. Accordingly, during normal operation in which the lubricating oil is sufficiently supplied, the lubricating oil always remains (exists) in the oil retaining recess.

  From this state, if the flow rate of the lubricating oil in the bearing inner space decreases or becomes zero due to, for example, a failure of the lubricating oil supply pump or leakage of the lubricating oil from the casing, the pocket side The feed of the lubricating oil from the opening of the oil into the oil retaining recess is reduced or stopped. In this way, in a state where the feeding of the lubricating oil from the opening is reduced or stopped, the lubricating oil that has already accumulated in the oil retaining recess is transferred from the oil retaining recess to the outer edge side of the large-diameter rim portion. It is not pushed out and stays in this oil retaining recess. Then, the lubricating oil remaining in the oil retaining recess enters into the recess formed in the end surface on the large diameter side of the tapered roller held in the pocket, and this large diameter is caused by the rotation of the tapered roller. It is sent to the sliding contact portion on the side end surface and the axially inner side surface of the large diameter rim portion, and the sliding contact portion is lubricated. The lubricating oil remaining in the oil retaining recess when the failure or leakage occurs can use a large portion of the lubricating oil for lubricating the sliding contact portion. Therefore, it is possible to sufficiently lengthen the time from the occurrence of the poor lubrication state until the rotation becomes impossible due to seizure. For this reason, the vehicle can be operated to a place where it does not get in the way, and the time required for the restoration of the railway can be shortened, and it is difficult to cause traffic congestion. Furthermore, the poor lubrication makes it difficult to cause the rotation support portion to become unrotatable, and it is difficult to induce failure of other portions, and it is difficult to cause problems such as cost and time required for repair.

  Further, since the tapered roller bearing having a contact angle of 20 ° or more has a larger contact angle, the applied radial load and thrust load are large, and lubrication failure during rotation is more likely to occur. When the bearing structure of the present invention is applied to a tapered roller bearing having a contact angle of 20 ° or more, the durability is improved in a poorly lubricated state, that is, the time from the poorly lubricated state until the rotation becomes impossible due to seizure. Extend more fully. In particular, the above-described structure of the cage and the rolling element can be suitably used for a tapered roller bearing having a contact angle of 25 ° or more.

  If the oil retaining recess is formed in a portion aligned with at least a part of the pocket, the axial direction of the large-diameter side collar portion passes through the recess formed on the large-diameter end surface of the tapered roller held in the pocket. Lubricating oil is supplied to the inner surface, and the sliding contact portion between the inner surface in the axial direction and the large-diameter side end surface of another tapered roller can also be lubricated. Accordingly, the oil retaining recesses can be provided, for example, in one or two pocket portions in the circumferential direction. However, as in the invention described in claim 3, the number of the oil retaining recesses is the same as the number of the pockets, and the oil retaining recesses provided independently of each other in the circumferential direction are respectively connected to the respective oil retaining recesses. If it is opened toward the pocket, the amount of lubricating oil accumulated in all the oil retaining recesses (the amount of lubricating oil that can be accumulated in the entire cage) is secured, and from the occurrence of poor lubrication to the inability to rotate This is advantageous in terms of lengthening the time.

  Further, as in the invention described in claim 4, the bottom portion of the oil retaining recess is inclined in a direction toward the radially outward direction toward the pocket, or as in the invention described in claim 4, If the inner peripheral surface of the large-diameter side rim portion is inclined in the direction toward the radially outward direction toward the pocket, the lubricating oil accumulated in the oil retaining recess, and further, the inner diameter of the large-diameter side rim portion Lubricating oil adhering to the peripheral surface can be efficiently guided toward the end surface on the large diameter side of each tapered roller. As a result, when a poor lubrication occurs, the lubricating oil remaining on the large-diameter end of the cage is removed from the large-diameter end surface of each tapered roller and the axial inner surface of the large-diameter flange. Can be effectively used for lubrication of the sliding contact portion, and the time from the occurrence of the poor lubrication state to the impossibility of rotation can be made longer.

The fragmentary sectional view of the tapered roller bearing which shows the 1st example of embodiment of this invention. The X section enlarged view of FIG. The perspective view shown in the state which took out the holder | retainer incorporated in the 1st example of embodiment and was seen from the large diameter side and radial direction outer side. The Y section enlarged view of FIG. The fragmentary sectional view of the tapered roller bearing which shows the 2nd example of embodiment of this invention. The X section enlarged view of FIG. The perspective view shown in the state which took out the holder | retainer incorporated in the 2nd example of embodiment and was seen from the large diameter side and radial direction outer side. The Y section enlarged view of FIG. The fragmentary sectional view of the tapered roller bearing which shows the 3rd example of embodiment of this invention. The partial cut perspective view which shows the 1st example of the general tapered roller bearing known conventionally. The fragmentary sectional view which shows the 2nd example. The perspective view similar to FIG. 3 which takes out and shows the holder | retainer integrated in this 2nd example. The Z section enlarged view of FIG. The fragmentary sectional view which shows the 1st example of the conventional structure in which the countermeasure for the seizure prevention was completed. The fragmentary sectional view which shows the 2nd example. The perspective view shown in the state which took out some cages built in this 2nd example and was seen from the large diameter side and radial direction outer side.

[First example of embodiment]
1-4 show a first example of an embodiment of the present invention corresponding to claims 1 and 3 to 4. The features of the present invention, including the structure of this example, are characterized by the fact that the poor-lubrication state occurs by devising the shape and structure of the large-diameter end of the cage and the large-diameter end of each tapered roller. This is in the point of extending the time until the rotation is impossible. The other basic configuration of the tapered roller bearing is the same as that of the conventionally known tapered roller bearing shown in FIGS. The overlapping description will be omitted or simplified, and the following description will focus on the features of this example and the parts that have not been described previously.

  The cage 5d constituting the tapered roller bearing 1 of this example is a so-called saddle type cage which is integrally formed by injection molding synthetic resin or by machining a metal material. Is formed in a partial conical cylindrical shape. There are no particular restrictions on the type of synthetic resin used for injection molding. For example, polyamide 66 (PA66), polyamide 46 (PA46), polyphenylene sulfide (PPS), etc., which are generally used for injection molding of cages made of synthetic resin. Various synthetic resins that have been used can be used. Any synthetic resin can be used alone or mixed with a reinforcing fiber such as carbon fiber or glass fiber or a ceramic whisker for reinforcement. Moreover, as a metal material, iron-type alloys, such as steel materials and stainless steel materials, copper-type alloys, such as brass, etc. can be used.

  In any case, in the large-diameter side rim portion 12a, the portion between the column portions 14a, 14a adjacent to each other in the circumferential direction, in other words, the phase in the circumferential direction coincides with each pocket 15a, 15a (each of these Oil retaining recesses 19 and 19 are provided on the inner peripheral surfaces of the portions (aligned with the large-diameter side ends of the pockets 15a and 15a), respectively. Each of these oil retaining recesses 19 and 19 has a claw shape when viewed in the radial direction (from the inner diameter side) of the cage 5d, and the width in the circumferential direction is wider toward the pockets 15a and 15a. These pockets become narrower as they move away from the pockets 15a and 15a. Further, the depth of the oil retaining recesses 19 and 19 with respect to the radial direction (thickness direction) of the cage 5d is deeper toward the pockets 15a and 15a, and gradually decreases with increasing distance from the pockets 15a and 15a. To do.

The depths of the oil retaining recesses 19, 19 are zero at the outer edge portion of the large diameter rim portion 12a. Therefore, these oil retaining recesses 19 and 19 are opened only on the inner diameter side of the cage 5d and the pockets 15a and 15a, and are not opened on both sides in the circumferential direction and on the outer side in the axial direction. Of the oil retaining recesses 19 and 19, the bottom portion which is the deepest portion in the width direction in the circumferential direction in the circumferential direction is radially outward toward the pockets 15a and 15a. Is inclined by an angle θ _{1 with} respect to the central axis of the cage 5d. In short, the oil retaining recesses 19, 19 are made deeper toward the center in the width direction and further toward the pockets 15a, 15a at the center in the width direction (in the axial direction). , 15a is inclined in a direction toward the radially outward direction of the cage 5d.

  Further, a recess 20 is formed at the center of the large-diameter end face 10 of each tapered roller 4a that is rotatably held in each of the pockets 15a, 15a. In the case of the illustrated example, the concave portion 20 is circular, but it may also be an annular shape (the central portion of the large-diameter side end face 10 is left without being recessed). In any case, the center of the recess 20 is positioned on the central axis of each tapered roller 4a. And the part opened to the inner surface of each said pocket 15a, 15a among the bottom surfaces of each said oil retaining recessed part 19 and 19 is the large diameter side end surface of the said tapered roller 4a hold | maintained in the said pocket 15a, 15a. 10 is made to face the recess 20 formed in 10. In addition, regarding the radial direction of each of these tapered rollers 4a, a portion (point A portion in FIG. 2) of the bottom of each of the oil retaining recesses 19 and 19 that opens to the inner surface of each of the pockets 15a and 15a It is located inside the outer peripheral edge of the recess 20. Accordingly, the inner surface side openings of the pockets 15 a and 15 a of the oil retaining recesses 19 and 19 are entirely opposed to the recess 20. For this reason, the lubricating oil which exists in each said oil retaining recessed part 19 and 19 and was pressed on the bottom part of each these oil retaining recessed parts 19 and 19 by the centrifugal force based on rotation of the said holder | retainer 5d has almost the whole quantity. , The pockets 15a and 15a tend to flow into the recess 20 through the openings on the inner surface side. The opening edge of each of the oil retaining recesses 19, 19 on the side of the pockets 15 a, 15 a is substantially flat on the flat portion of the large-diameter side end surface 10 that is located around the recess 20. Thus, they face each other through sliding contact or a minute gap. Accordingly, the lubricating oil that has flowed into the concave portion 20 flows outward in the radial direction of the tapered roller 1 regardless of the centrifugal force based on the revolving motion of each tapered roller 4a or the rotational motion of the cage 5d. Hateful.

  During operation of the rotary machine device incorporating the tapered roller bearing of the present example configured as described above, the lubricating oil is pumped to the inner peripheral surface of the outer ring 2 by the pumping action based on the centrifugal force associated with the revolving motion of each tapered roller 4a. A bearing internal space 21 between the inner ring 3 and the outer peripheral surface flows from the small diameter side to the large diameter side of the outer ring raceway 6 and the inner ring raceway 7 (from the upper left to the lower right in FIG. 1). When the supply amount of the lubricating oil is sufficient, the lubricating oil flowing in the bearing inner space 21 in this way is the large diameter side end surface 10 of each tapered roller 4 a and the large diameter side of the outer peripheral surface of the inner ring 3. The sliding contact portion with the axially inner side surface 11 of the large-diameter side flange portion 8 provided at the end portion is sufficiently lubricated. In this state, a part of the lubricating oil flowing in the bearing inner space 21 is in the oil retaining recesses 19 and 19 formed at a plurality of locations on the inner peripheral surface of the large-diameter side rim portion 12a. While flowing in from the opening on the side of each pocket 15a, 15a, it is discharged to the outer edge side in the axial direction of the large-diameter side rim portion 12a. That is, the lubricating oil that has entered the oil retaining recesses 19 and 19 previously flows from the respective oil retaining recesses 19 and 19 by the lubricating oil newly flowing from the openings on the pockets 15a and 15a side. Extruded. Therefore, during normal operation in which the lubricating oil is sufficiently supplied, the lubricating oil is always accumulated (exists) in each of the oil retaining recesses 19 and 19.

  From this state, when the flow rate of the lubricating oil in the bearing internal space 21 decreases or becomes zero due to, for example, a failure of the lubricating oil supply pump or leakage of the lubricating oil from the casing, The feeding of the lubricating oil into the oil retaining recesses 19 and 19 from the openings on the pockets 15a and 15a side is reduced or stopped. In this way, when the feeding from the opening is reduced or stopped, the lubricating oil that has already accumulated in the oil retaining recesses 19, 19 is transferred from the oil retaining recesses 19, 19 to the large-diameter rim. It is not pushed out to the outer edge side of the part 12a, and remains in each of these oil retaining recesses 19 and 19. In this state, the lubricating oil in each of the oil retaining recesses 19 and 19 tends to be pressed against the bottom surface of each of the oil retaining recesses 19 and 19 due to the centrifugal force accompanying the rotation of the cage 5d. Since the bottom surfaces of the oil retaining recesses 19 and 19 are inclined with respect to the width direction and the axial direction as described above, most of the lubricating oil remaining in the oil retaining recesses 19 and 19 Of the recesses 20 formed in the large-diameter end surface 10 of the tapered rollers 4a held in the pockets 15a and 15a, the tapered roller bearing 1 enters an outer portion in the radial direction. Then, the lubricating oil that has entered the recess 20 is brought into contact with the sliding contact portion between the large-diameter side end surface 10 and the large-diameter-side rim portion 12a in the axial direction along with the rotation of the tapered rollers 4a. It is sent (soaks into this sliding contact portion) and lubricates this sliding contact portion.

  As is clear from the above description, the lubricating oil remaining in each of the oil retaining recesses 19 and 19 at the time of occurrence of the failure or leakage is used for lubrication of the sliding contact portion. it can. Therefore, it is possible to sufficiently lengthen the time from the occurrence of the poor lubrication state until the rotation becomes impossible due to seizure. According to the seizure experiment by oil dipping performed by the present inventor, the tapered roller bearing having the structure shown in FIGS. 1 to 4 is less exhausted than the conventional structure shown in FIGS. The time required for image sticking to be increased by about three times. For this reason, if measures such as detecting the occurrence of poor lubrication with sensors are taken, measures such as slowing down the operating speed or stopping in a safe state can be taken with sufficient margin before seizure occurs. It becomes possible. And before the burn-in occurs, the vehicle can be operated to a place where it does not get in the way, so that the time required for the restoration of the railway can be shortened and it is difficult to cause traffic congestion. Furthermore, the poor lubrication makes it difficult to cause the rotation support portion to become unrotatable, and it is difficult to induce failure of other portions, and it is difficult to cause problems such as cost and time required for repair.

[Second Example of Embodiment]
FIGS. 5-8 has shown the 2nd example of embodiment of this invention corresponding to Claims 2-4. In the case of this example, a so-called steeply tapered cone having an angle of 25 ° formed by a tangent line formed by bringing the outer ring raceway 6 and the rolling surface of the tapered roller 4a into contact with each other and the rotating shaft of the bearing. This is an example applied to a roller bearing.

  The larger the contact angle of the tapered roller bearing 1, the larger the load applied to the sliding surface of the large-diameter side end face 10 of the roller 4a and the axial side face 11 of the large-diameter side flange 8 of the inner ring 3, and the oil film is insufficient. Prone to tend. Accordingly, in such a tapered roller bearing with a contact angle of 20 ° or more, particularly with a contact angle of 25 ° or more, the large-diameter side end face 10 and the large-diameter side flange 8 are likely to seize. Therefore, in this embodiment, by adopting the same structure of the cage as in the first example of the embodiment, the wear resistance and seizure resistance effect of the steep tapered roller bearing can be further improved.

  In addition, since it is the same as that of the 1st example of embodiment regarding the structure and effect | action except that the bearing of this embodiment is a steep tapered roller bearing with a contact angle of 25 degrees, the same code | symbol is used. The overlapping illustrations and explanations are omitted.

[Third example of embodiment]
FIG. 9 shows a third example of the embodiment of the invention corresponding to claims 1 to 5. In the case of this example, not only the bottom portion of the oil retaining recess 19 formed in the inner peripheral surface of the large-diameter side rim portion 12b and the portion that aligns with each pocket 15a, but also the circumferential disengagement from each of these oil retaining recesses 19. The original inner peripheral surface of the large-diameter side rim portion 12b is also inclined by an angle θ _{2 with} respect to the central axis of the retainer 5e in the radially outward direction toward each pocket 15a. According to such a structure of the present example, not only the oil retaining recess 19 but also the lubricating oil adhering to the inner peripheral surface of the large-diameter side rim portion 12b, each retained in each pocket 15a. It can guide efficiently toward the large diameter side end face 10 of the tapered roller 4a. As a result, when a poor lubrication state occurs, the lubricating oil remaining at the large-diameter end of the cage 5e is transferred to the large-diameter end surface 10 of each tapered roller 4a and the large outer peripheral surface of the inner ring 3. It can be effectively used for lubrication of the sliding contact portion of the large-diameter side flange portion 8 provided at the radial side end portion with the axially inner side surface 11, and the time from the occurrence of the poor lubrication state to the impossibility of rotation becomes longer. it can. Since the configuration and operation of other parts are the same as in the case of the first example of the embodiment described above, overlapping illustrations and descriptions are omitted.

  The cage shape of this embodiment can also be applied to the steep tapered roller bearing of the second example of the above-described embodiment.

DESCRIPTION OF SYMBOLS 1 Tapered roller bearing 2 Outer ring 3 Inner ring 4, 4a Tapered roller 5, 5a, 5b, 5c, 5d, 5e Cage 6 Outer ring track 7 Inner ring track 8 Large diameter side flange 9 Small diameter side flange 10 Large diameter side end surface 11 Axis Directional inner surface 12, 12a, 12b Large diameter side rim portion 13, 13a Small diameter side rim portion 14, 14a Column portion 15, 15a Pocket 16 Bending plate portion 17, 17a Oil retaining portion 18 Partition plate portion 19 Oil retaining recess 20 Recessed portion 21 Bearing internal space

Claims (5)

  An outer ring having a conical concave outer ring raceway on the inner peripheral surface, a conical convex inner ring raceway on the outer peripheral surface and concentric with the outer ring on the inner diameter side of the outer ring, and a large diameter side end of the inner ring raceway An inner ring having a large-diameter side flange projecting outward in the radial direction from the portion, and is arranged to freely roll between the inner ring raceway and the outer ring raceway, and the respective large-diameter side end faces of the large-diameter side collar Provided with a plurality of tapered rollers opposed to the axial side surface of the portion and a cage for holding each of the tapered rollers, the cages being arranged concentrically and spaced apart in the axial direction. A large-diameter side rim portion and a small-diameter side rim portion each having an annular shape, and a plurality of pillar portions spanned between the two rim portions, and both the rim portions and the circumferential direction Each part surrounded by a pair of pillars adjacent to each other In the tapered roller bearing that has a structure as a pocket for holding each tapered roller, the phase in the circumferential direction is at least a part of the pocket in the large-diameter side rim portion. An oil retaining recess recessed radially outward is provided on the inner peripheral surface portion of the portion aligned with the pocket, and the portion of the bottom surface of the oil retaining recess that opens to the inner surface of the pocket is the pocket. A tapered roller bearing characterized in that the tapered roller bearing is opposed to a recess formed in an end surface on the large diameter side of the tapered roller held inside.   The tapered roller according to claim 1, wherein an angle formed by a tangent line formed by contacting a raceway surface of the outer ring and a rolling surface of the tapered roller and a rotation axis of the bearing is 20 ° or more. bearing.   The number of oil retaining recesses is the same as the number of pockets, and each of these oil retaining recesses provided independently of each other in the circumferential direction is opened toward each of the pockets. Tapered roller bearings described in 1.   The tapered roller bearing according to any one of claims 1 to 3, wherein a bottom portion of the oil retaining recess is inclined in a radially outward direction toward the pocket.   The tapered roller bearing according to any one of claims 1 to 4, wherein an inner peripheral surface of the large-diameter side rim portion is inclined in a direction toward a radially outward direction toward the pocket.

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