JP4973379B2 - Double-row cylindrical roller bearing device for railway vehicle axles - Google Patents

Description

The present invention relates to a rolling bearing device used in oil bath lubrication, and more particularly , to a double row cylindrical roller bearing device for a railway vehicle axle according to an improvement of a bearing for a railway vehicle axle .

  At present, as a rolling bearing device used in oil bath lubrication, for example, a lubrication method using oil bath lubrication is often used for a railway vehicle axle bearing. As an example, Patent Document 1 discloses that a front lid-side annular flow channel section and a rear lid-side annular flow channel for circulating oil as a lubricant through an oil reservoir in an axle box that covers the outer ring outer periphery. A railway vehicle is shown in which the parts have the same volume. Patent Document 2 discloses a cylindrical roller bearing device that circulates oil, which is a lubricant, through an oil passage channel by a slinger effect using centrifugal force during bearing rotation.

Incidentally, various railway vehicle axle bearings including Patent Documents 1 and 2 are continuously used in a high-speed rotation environment. For this reason, depending on the magnitude of the agitation resistance of the lubricant (oil) that is agitated as the bearing rotates at high speed, the circulation efficiency of the lubricant (oil) decreases, and the lubricant (oil) and the bearing In some cases, the cooling performance of the bearing by heat exchange can be kept constant. In this case, the amount of heat generated around the bearing increases, and the temperature of the bearing rises beyond an allowable range. As a result, it becomes difficult to maintain the lubrication performance of the bearing constant over a long period of time, and as a result, the bearing may deteriorate early or the lubricant (oil) may leak to the outside of the bearing. .
JP 2006-83945 A Japanese Patent Laid-Open No. 11-230178

  The present invention has been made to solve such problems, the purpose of which is to improve the cooling efficiency and lubrication performance that can suppress the temperature rise of the bearing by improving the circulation efficiency of the lubricant (oil) An object of the present invention is to provide a rolling bearing device excellent in the above.

To achieve the above object, the present invention includes an inner ring which rotates with the shaft, is disposed opposite to the inner ring, an outer ring of the double row which is fitted to the axle box, rollably in double rows between the inner and outer rings and a plurality of rollers incorporated in the outer ring, the flange portion is provided to hold and guide the plurality of rollers from both sides, the inner ring and the oil thrower member mated shaft end nut to said shaft is positioned and fixed in a sandwich state between, and, a double row cylindrical roller bearing device for a railway vehicle axle used in an oil bath lubrication, wherein the inner ring, at a position adjacent to the shaft end nut, the with flange wheels with projections of large diameter than the outer diameter of the shaft end nut is provided, at a position adjacent to the oil cutting member, greater than the outer diameter of the inner ring outer diameter and the oil cut member ring member having a diameter provided, the outer ring The outer ring spacer is configured and disposed, and the outer ring spacer is formed with a grooving groove whose outer periphery is continuously depressed along the circumferential direction, and is located at least in the oil bath. A plurality of through holes formed through the outer ring spacer in the radial direction are provided, and the axle box is configured with an oil reservoir for storing lubricating oil, and both axial sides of the oil reservoir, A front lid side oil passage and a rear lid side oil passage formed between the outer ring and the axle box are provided, and during the rotation of the bearing, the lubricating oil has a protruding portion of the collar ring having a large diameter and By being forced to return to the ring member, the oil flows from the oil reservoir through the through hole and flows between the inner and outer rings, and then branches in two directions along the axial direction. Each is guided to the member, then each said front lid The lubricating oil that has been returned to the oil reservoir through the oil passage and the rear lid-side oil passage and that has been discharged through the through-hole due to centrifugal force when the bearing rotates is circumferentially along the groove. And is introduced into the oil reservoir .
In the present invention, the through hole located in the oil bath of the outer ring spacer has a long hole shape.

  ADVANTAGE OF THE INVENTION According to this invention, the rolling bearing apparatus excellent in the cooling performance and the lubrication performance which can suppress the temperature rise of a bearing by improving the circulation efficiency of lubricant (oil) is realizable.

  Hereinafter, a rolling bearing device according to an embodiment of the present invention will be described with reference to the accompanying drawings. In the present embodiment, description will be made assuming a railway vehicle axle bearing as an example of a rolling bearing device.

  FIG. 1 (a) shows a double-row cylindrical roller bearing used in oil bath lubrication as a railway vehicle axle bearing. The double-row cylindrical roller bearing rotates together with a shaft (railway vehicle axle) Ax. The inner ring 2, the outer rings 4a and 4b arranged opposite to the inner ring 2, and the raceway surfaces 2s and 4s formed in double rows on the opposing surfaces of the inner ring 2 and the outer rings 4a and 4b in the circumferential direction. A plurality of rolling elements (rollers) 6 incorporated so as to roll freely, and a plurality of rolling elements (rollers) 6 revolve along the inner and outer rings 2, 4a, 4b while holding the rolling elements (rollers) 6 one by one. A cage 8 is provided.

  In this bearing, a single (integrated) inner ring 2 is fitted to the railcar axle Ax, and a plurality (two as an example in the drawing) of outer rings 4a and 4b are opposed to the outer side of the inner ring 2. It is fitted (fixed) to the annular shaft box 10. In this case, the outer rings 4a and 4b are arranged in a double row with the outer ring spacer 12 interposed therebetween, and the raceway surface 4s (that is, the outer ring raceway) is formed on the opposing surface (inner circumference) of each outer ring 4a and 4b. A surface 4s) is formed. On the other hand, the single inner ring 2 has a raceway surface 2s (that is, an inner ring raceway surface 2s) formed on an opposing surface (outer periphery) facing the double row outer ring raceway surface 4s.

  In addition, annular outer ring collar portions 4t are respectively provided on both sides of the two outer ring raceway surfaces 4s along the raceway surface 4s. On the other hand, on both sides of one inner ring raceway surface 2s, the raceway is provided. An annular inner ring collar portion 2t protrudes along the surface 2s. In this case, the inner ring 2 is positioned and fixed in a state of being sandwiched between the shaft end nut 14 fitted to the railcar axle Ax and the oil draining member 16 and adjacent to the shaft end nut 14 of the inner ring 2. At this position, there is provided a collar 18 integrally formed with one inner ring collar 2t, and at the position adjacent to the oil draining member 16 of the inner ring 2, the other inner ring collar 2t protrudes. Has been.

  In such a configuration, the two outer rings 4a and 4b arranged in a double row via the outer ring spacer 12 are fixed in a state of being sandwiched between the front lid 20 and the rear lid 22 fitted to the axle box 10. Has been. In this case, the rear lid 22 is positioned by being fitted to the oil draining member 16 fitted to the railcar axle Ax. In this state, the inner ring 2 is applied to the oil draining member 16 by the shaft end nut 14 and tightened with the bolt 24, whereby the inner ring 2 is fitted (fixed) to the axle box 10 in the double row outer rings 4a, 4b. The collar 18 can be fixed to the railcar axle Ax, and the collar 18 can be positioned and fixed while being sandwiched between the shaft end nut 14 and the inner ring 2.

  The front lid 20 is fitted to the axle box 10 so as to cover the entire shaft end side of the railway vehicle axle Ax. On the other hand, foreign matter (water or water) is interposed between the rear lid 22 and the oil draining member 16. A sealing mechanism is constructed to prevent intrusion of dust and the like and to prevent leakage of lubricant (oil) described later. In this case, an oil seal 26 and a labyrinth seal 28 are used in combination as a sealing mechanism between the rear lid 22 and the oil draining member 16, and the types and shapes of these seals 26 and 28 are, for example, those of the bearing. Since it is arbitrarily set according to the purpose of use and usage environment, there is no particular limitation here. Moreover, in order to further improve the sealing performance with respect to the bearing, it is preferable to interpose, for example, an O-ring 30 at each part where the front lid 20 and the rear lid 22 and the axle box 10 are fitted.

  In this state, when the railway vehicle axle AX is rotated, the cage is placed between the raceway surfaces 2s and 4s of the inner and outer rings 2, 4a and 4b while the inner and outer rings 2, 4a and 4b rotate relative to each other (bearing is rotating). A plurality of rolling elements (rollers) 6 incorporated together with 8 roll along the raceway surfaces 2s and 4s while being held and guided by the flange portions 2t and 4t. At this time, in order to maintain the lubrication performance constant during the rotation of the bearing and realize smooth rotation performance, the cylindrical roller bearing is provided with an oil bath lubrication configuration for using oil bath lubrication.

  In the oil bath lubrication configuration, a shaft box oil reservoir 10g for storing a predetermined amount of lubricant (oil) is disposed on the lower side (lower side in the figure) of the inner periphery of the axle box 10 in double rows of outer rings 4a, 4b. It is provided opposite to. In this case, the axle box oil reservoir 10g is provided vertically below in a state where the rolling bearing device (double-row cylindrical roller bearing) is set on the railcar axle Ax extending in the horizontal direction. As a result, the lubricant (oil) enclosed in the rolling bearing device always flows into the axle box oil reservoir 10g due to its own weight. It should be noted that the amount of lubricant (oil) enclosed is the position where the oil surface (not shown) exceeds the lowest outer ring collar 4t of the double row cylindrical roller bearing when the bearing is stationary (non-rotating) ( In short, it is preferable to set so that the outer ring raceway surface 4s is positioned at a position where the outer ring raceway surface 4s is immersed in oil.

  A front lid side oil passage 10a and a rear lid side oil passage 10b are formed on both sides of the axle box oil reservoir 10g. The front lid side oil passage 10a is configured between the outer ring 4a near the front lid 20 and the axle box 10, and the front lid interior 20p (the shaft end of the front lid 20, the double row cylindrical roller bearing, and the railcar axle Ax). (Area surrounded by). On the other hand, the rear lid side oil passage 10b is configured between the outer ring 4b near the rear lid 22 and the axle box 10, and the rear lid inside 22p (the rear lid 22, the oil draining member 16, the axle box 10, and the double row is formed. A region surrounded by the cylindrical roller bearing).

  A partition plate for blocking the flow of the lubricant (oil) is not provided between the oil seal 26 and the double row cylindrical roller bearing inside the rear lid.

  In such a rolling bearing device (double-row cylindrical roller bearing), the collar ring 18 that is positioned and fixed in a state of being sandwiched between the shaft end nut 14 and the inner ring 2 has an outer diameter of the shaft end nut 14. A protrusion 18t having a large diameter is also provided. Further, a ring member 32 is interposed between the oil draining member 16 and the inner ring 2, and the ring member 32 is positioned and fixed while being sandwiched between the oil draining member 16 and the inner ring 2. Yes. The ring member 32 has a diameter larger than the outer diameter of the inner ring (the outer diameter of the inner ring collar portion 2t) and the outer diameter of the oil draining member 16.

  Two protrusions 18t provided on the collar ring 18 are illustrated on the drawing (see FIG. 3A). For example, as shown in FIGS. 3B and 3C, one protrusion 18t is provided. A (single) protrusion 18t may be used. In this case, the protrusion 18t in FIG. 5B is tapered along the flow direction Fa of the lubricant (oil), which will be described later, thereby improving the circulation efficiency of the lubricant (oil). Yes. Further, the protrusion 18t in FIG. 5C has a rectangular shape, but even such a shape does not affect the circulation efficiency of the lubricant (oil). Furthermore, as shown in FIG. 5C, two protrusions 18t having a difference in height may be provided so that the upstream side is low and the downstream side is high along the flow direction Fa of a lubricant (oil) described later. .

  In this case, in the collar ring 18, the height difference between the collar height of the collar part 2 t and the projection part diameter of the projection part 18 t is, for example, the type of lubricant (oil) (for example, viscosity) or the lubricant during rotation of the bearing. Since it is arbitrarily set according to the circulation speed of (oil) or the purpose and environment of use of the bearing, it is not particularly limited here. Further, the number of collar portions 2t is not limited to two, and may be three or more. In short, as long as the protrusion 18t has a diameter larger than the outer diameter of the shaft end nut 14, the number and shape thereof are not limited.

  On the other hand, although one ring member 32 is illustrated on the drawing, it is not limited to this and may be two or more. In this case, the shape of the ring member 32 may be tapered along the lubricant (oil) flow direction Fa, which will be described later, in the same manner as the collar portion 2t described above, and the upstream side is low and the downstream side is high. Moreover, you may comprise the two ring members 32 which gave the height difference mutually. In short, as long as the ring member 32 has a diameter larger than the outer diameter of the oil draining member 16, the number and shape thereof are not limited.

  Further, the collar ring 18 and the ring member 32 described above may be formed separately from the inner ring 2 or may be formed integrally with the inner ring 2. In the case where the collar ring 18 and the ring member 32 are configured separately from the inner ring 2, the material of the collar ring 18 and the ring member 32 may be, for example, either metal or nonmetal, but should be nonmetal. Thus, the weight of the entire bearing can be reduced.

  Further, as shown in FIG. 4 (a), the outer ring spacer 12 is formed with a grooving groove 12g whose outer periphery is partially recessed along the circumferential direction. A plurality of through-holes 12h formed so as to penetrate in the radial direction are provided along the grooving groove 12g at predetermined intervals (for example, at equal intervals). In this case, the size (hole diameter) and number of each through hole 12h are, for example, the size (width dimension, circumferential length) of the outer ring spacer 12 and the grooving groove 12g, or the type of lubricant (oil) ( For example, since it is arbitrarily set according to the viscosity) and the circulation speed of the lubricant (oil) during rotation of the bearing, there is no particular limitation here.

  Further, the shape of the plurality of through holes 12h is not limited to a circular round hole, but is a long through hole 12h (see FIG. 4B) extended by a predetermined amount along the grooving groove 12g. Also good. Further, for example, as shown in FIG. 4B, a long hole-shaped through hole 12h and a round hole-shaped through hole 12h may be mixed. In this case, when the outer ring spacer 12 is interposed between the outer rings 4a and 4b, it is preferable that the elongated hole-shaped through hole 12h is positioned so as to face the axle box oil reservoir 10g.

  As described above, the axle box oil reservoir 10g is provided vertically below the rolling bearing device (double-row cylindrical roller bearing) set on the railcar axle Ax extending in the horizontal direction. . For this reason, the lubricant (oil) sealed in the rolling bearing device is caused to pass through the elongated hole-shaped through hole 12h by its own weight by making the elongated hole-shaped through hole 12h face the axle box oil reservoir 10g. It can smoothly flow into the axle box oil reservoir 10g.

  Further, the groove groove 12g formed on the outer periphery of the outer ring spacer 12 moves the lubricant (oil) discharged from the through hole 12h by the centrifugal force during the rotation of the bearing in the circumferential direction along the groove groove 12g. Thus, it has a function of smoothly introducing into the shaft box oil reservoir 10g. Further, the plurality of through holes 12h have a function of collecting the lubricant (oil) stirred during the rotation of the bearing toward the axle box oil reservoir 10g, and at the same time, the lubricant (oil) from the axle box oil reservoir 10g. It has the function of supplying (circulating) oil toward the inside of the bearing.

  According to such a rolling bearing device (double-row cylindrical roller bearing), when the collar ring 18 and the ring member 32 on both sides of the inner ring 2 rotate together with the railway vehicle axle Ax during the bearing rotation, the lubrication enclosed in the shaft box 10 is performed. A slinger effect acts on the agent (oil), thereby forcibly circulating the lubricant (oil) along the axial direction. At this time, the lubricant (oil) in the oil reservoir 10g of the axle box flows between the inner and outer rings 2, 4a, 4b from the respective through holes 12h of the outer ring spacer 12, and then the flow direction is 2 along the axial direction. Branch in the direction. In this case, in one flow direction Fa, the lubricant (oil) is recirculated toward the collar 18, and in the other flow direction Fb, the lubricant (oil) is recirculated toward the ring member 32.

  Here, the collar ring 18 is provided with a protrusion 18t having a diameter larger than the collar height of the collar portion 2t and the outer diameter of the shaft end nut 14, thereby amplifying the slinger effect and the lubricant. (Oil) is strongly guided toward the collar 18 and refluxed. As a result, the lubricant (oil) that has been guided to the collar ring 18 and circulated is returned to the axle box oil reservoir 10g from the front lid side oil passage 10a after passing through the front lid interior 20p.

  On the other hand, the ring member 32 has a diameter larger than the inner ring outer diameter (the outer diameter of the inner ring collar portion 2t) and the outer diameter of the oil draining member 16. In this case, since the ring member 32 has a larger diameter than the outer diameter of the inner ring collar portion 2t, the slinger effect is amplified, and the lubricant (oil) is strongly guided toward the ring member 32 and is refluxed. As a result, the lubricant (oil) guided and circulated to the ring member 32 passes through the rear lid interior 22p and then returns to the axle box oil reservoir 10g from the rear lid side oil passage 10b. Furthermore, since the ring member 32 has a diameter larger than the outer diameter of the oil draining member 16, the lubricant (oil) guided to the ring member 32 and circulated is shaken off by the ring member 32. Thereby, excessive penetration of the lubricant (oil) into the oil seal 26 is prevented, and as a result, leakage of the lubricant (oil) from the oil seal 26 is prevented.

  Thus, the lubricant (oil) returned from the front lid side oil passage 10a and the rear lid side oil passage 10b to the axle box oil reservoir 10g is caused by the slinger effect accompanying the rotation of the collar ring 18 and the ring member 32. It flows again between the inner and outer rings 2, 4a, 4b from the respective through holes 12h of the outer ring spacer 12. As a result, a circulation path of the lubricant (oil) is formed inside the axle box 10, and the lubricant (oil) can be circulated along the circulation path.

  In this case, the circulation path of the lubricant (oil) inside the axle box 10 is forced to circulate the lubricant (oil) forcibly and smoothly, so that it is affected by the stirring resistance of the lubricant (oil) during the rotation of the bearing. Therefore, the circulation efficiency of the lubricant (oil) can be kept constant and improved. For this reason, it is possible to maintain and improve the cooling performance of the bearing by heat exchange between the lubricant (oil) and the bearing.As a result, the amount of heat generated around the bearing is reduced, and the temperature of the bearing is within an allowable range. Can be maintained. Thereby, since the lubrication performance of the bearing can be maintained constant over a long period of time, the bearing can be used continuously and stably over a long period of time.

  Here, considering the relationship between the change in the rotational speed of the bearing and the temperature rise of the outer rings 4a and 4b, as shown in FIG. 2 (a), the bearing device according to the present embodiment (Example 1) is a conventional product. It can be seen that the temperature rise accompanying the increase in the rotational speed is smaller than Also, considering the relationship between the axial position of the lubricant (oil) circulating in the bearing (positions PA, PB, PC in FIG. 1B) and the temperature rise, as shown in FIG. 2B, At the position PB in the vicinity of the outer ring spacer 12 of the axle box oil reservoir 10g, the temperature rises compared to the conventional product, but at other positions, the bearing device according to the present embodiment (Example 1) is the conventional product. It can be seen that the temperature rise is small compared to. Thereby, it was demonstrated that the bearing device according to the present embodiment improves the heat exchange efficiency and is excellent in cooling performance.

  In the present embodiment, the lubricant (oil oil) guided to the ring member 32 and circulated by extending the rear lid side oil passage 10b to a position facing the ring member 32 or a position exceeding the position in the axial direction. ) Can be more efficiently introduced into the shaft box oil reservoir 10g.

  Further, in the present embodiment, the ring member 32 also has a function as a partition plate that reliably stops the recirculation of the lubricant (oil) in the axial direction that occurs suddenly in the use state of the bearing. This eliminates the need for a partition plate for blocking the flow of the lubricant (oil). As a result, it is possible to reduce the manufacturing cost of the bearing by reducing the number of parts.

  Further, in the present embodiment, the rolling bearing device is not limited to the double row cylindrical roller bearing. For example, the same effect can be realized by applying the above-described configuration to the double row tapered roller bearing. can do.

  Moreover, in this Embodiment, although the case where the said protrusion part 18t was provided in the collar ring 18 was assumed, it is not limited to this. For example, without providing the collar ring 18, the inner ring collar portion 2 t protrudes on both sides of the inner ring raceway surface 2 s, and one inner ring collar portion 2 t (the inner ring collar portion 2 t at a position adjacent to the shaft end nut 14) The protrusion 18t may be provided.

(a) is sectional drawing which shows the structure of the rolling bearing apparatus which concerns on one embodiment of this invention, (b) is sectional drawing which expands partially the structure around the inner and outer ring | wheels of the same figure (a). (a) is a figure which shows the relationship between the rotation speed change of a bearing, and the temperature rise of an outer ring | wheel, (b) is a figure which shows the relationship between the axial direction position of the lubricant (oil) circulating in the bearing, and a temperature rise. . (a)-(d) is sectional drawing which respectively shows the shape of the projection part provided in the collar ring. It is a figure which shows the structure of the outer ring | wheel spacer provided in the rolling bearing apparatus, Comprising: (a) is a front view, (b) is a side view, (c) is a perspective view. It is a figure which shows the other structure of the outer ring | wheel spacer provided in the rolling bearing apparatus, Comprising: (a) is a front view, (b) is a side view, (c) is a perspective view.

Explanation of symbols

2 inner ring
4a, 4b Outer ring 6 Rolling element 14 Shaft end nut 16 Oil draining member 18 Collar wheel 18t Protrusion 32 Ring member Ax Shaft (Railway vehicle axle)

Claims (2)

Comprising an inner ring which rotates with the shaft, it is disposed opposite to the inner ring, an outer ring of the double row which is fitted to the journal box, and a plurality of rollers incorporated in rollably in double rows between the inner and outer rings, the outer ring , the flange portion is provided to hold and guide the plurality of rollers from both sides, the inner ring is positioned and fixed in a state of being sandwiched between the mated shaft end nut and oil thrower member to the shaft, And a double-row cylindrical roller bearing device for railway vehicle axles used in oil bath lubrication,
Wherein the inner ring, at a position adjacent to the shaft end nut with flange wheels with projections of large diameter than the outer diameter of the shaft end nut is provided, at a position adjacent to the oil cutting member , the ring member is provided having a larger diameter than the outer diameter of the inner ring outer diameter and the oil cut member,
The outer ring is configured and disposed with an outer ring spacer interposed therebetween, and the outer ring spacer is formed with a grooving groove whose outer periphery is continuously recessed along the circumferential direction, and at least in an oil bath. A plurality of through holes formed through the outer ring spacer located in the radial direction are provided,
The axle box includes an oil reservoir for storing lubricating oil, and a front lid side oil passage and a rear lid formed on both sides in the axial direction of the oil reservoir and formed between the outer ring and the axle box. Side oil passages are provided,
During the rotation of the bearing, the lubricating oil is forced to flow back to the protruding portion of the collar ring and the ring member having a large diameter, so that the lubricating oil flows between the inner and outer rings through the through hole. Then, it branches in two directions along the axial direction and is guided to the projection and the ring member, respectively, and then returns to the oil reservoir through the front lid side oil passage and the rear lid side oil passage, respectively. As
When the bearing rotates, the lubricating oil discharged through the through holes by centrifugal force, double railcar axle, characterized in that it is allowed to introduce into the grooving the oil reservoir portion to move circumferentially along the groove Row cylindrical roller bearing device . The double-row cylindrical roller bearing device for a railway vehicle axle according to claim 1, wherein the through hole located in the oil bath of the outer ring spacer has a long hole shape.

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