JP2010007822A - Bearing arrangement for railway vehicle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a bearing arrangement for a railway vehicle capable of continuing to use the bearing over a long period continuously by intending to prevent an outer race from turning with respect to a housing without questioning any magnitude of creep force. <P>SOLUTION: The bearing arrangement is provided with an inner ring (rotating ring) 3 attached to an axle of the railway vehicle, an outer ring (stationary ring) 1 which is oppositely disposed outside the inner ring and on which the housing is attached, a sealed mechanism sealing interior of a bearing and a sensor 30 which detects relative rotation between the inner and outer rings. The sealed mechanism includes an annular sealing structure 25a adapted to extend so as to cover the interior of the bearing in such a state that the base end Pe is fitted in the outer ring and is provided so that at least one protuberance F1 which is projected toward housing H1 direction forms as one piece construction with the sealing structure on the outer periphery of the sealing structure. In the state of attaching the housing to the outer ring, the bearing arrangement is intended to prevent the outer ring from rotating with respect to the housing by the protuberance engaging to a rib structure R1 of the housing when force attempting to rotate the outer ring when the inner and outer rings relatively rotate occurs. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a railway vehicle bearing device in which rotation (creep) prevention of an outer ring with respect to a housing is achieved, for example.

  Conventionally, a railway vehicle bearing device includes an inner ring and an outer ring that are opposed to each other so as to be relatively rotatable, and a plurality of rolling elements that are rotatably incorporated between the inner and outer rings. The outer ring is attached to the housing of the bearing device and maintained in a non-rotating state. In the bearing device, the outer ring is provided with a sealing mechanism (for example, a seal) for sealing the inside of the bearing, and the seal is provided with a sensor for detecting the relative rotation of the inner and outer rings.

  By the way, in the bearing device as described above, a creeping force for rotating the outer ring may be generated while the vehicle is traveling (that is, during the relative rotation of the inner and outer rings). As a cause of the generation of such a creep force, for example, a cause due to relative movement between the housing and the outer ring or a cause caused by rotation of the outer ring due to friction inside the bearing can be cited.

  In any case, when the outer ring is rotated (creeped) with respect to the housing by the creep force, the seal provided on the outer ring is rotated accordingly. The sensor provided rotates in the same way. In this case, for example, the sensor collides with the housing, the sensor is damaged depending on the magnitude of the collision force at that time, or the cable connected to the sensor rotates, and the cable is disconnected depending on the amount of rotation. There is a risk of doing. Therefore, various measures are taken in order to prevent the outer ring from rotating relative to the housing.

  As an example, Patent Document 1 provides an engagement portion on a seal case of a sealing mechanism, and an engagement portion that can be engaged with the engagement portion on each of the outer ring and the housing. A technique for preventing rotation of the outer ring by engaging the engaging portions with each other is shown.

However, in such a conventional technique, the creep force for rotating the outer ring is directly applied to the engaging portion of the seal case, so that the engaging portion is damaged depending on the magnitude of the load at that time. There is a case. In this case, it becomes difficult to maintain the function as a sealing mechanism, and as a result, foreign matters (for example, broken pieces of the engaging portion, dust) enter the bearing or are enclosed in the bearing. There is a risk that the lubricant may leak to the outside. If it becomes so, it will become impossible to continue using a bearing continuously over a long period of time.
JP 2003-49831 A

  The present invention has been made to solve such a problem, and its purpose is to prevent the outer ring from rotating relative to the housing, regardless of the magnitude of the creep force, and to maintain the bearing for a long period of time. It is an object of the present invention to provide a railway vehicle bearing device that can be used continuously.

In order to achieve this object, the present invention provides a rotating wheel mounted on a rotating shaft of a railway vehicle, a stationary wheel disposed opposite to the rotating wheel and mounted with a housing of a bearing device, a rotating wheel, and a stationary wheel. A bearing device for a railway vehicle comprising a sealing mechanism that seals the inside of the bearing formed between the outside of the bearing and a sensor for detecting relative rotation between the rotating wheel and the stationary wheel. The mechanism has an annular seal structure extending so as to cover the inside of the bearing in a state where the base end portion is fitted to the stationary ring, and the outer periphery of the seal structure is directed toward the housing. At least one protruding portion that protrudes is provided integrally with the seal structure, and the stationary wheel is rotated when the rotating wheel and the stationary wheel rotate relative to each other when the housing is mounted on the stationary wheel. When force is generated, By protrusion Le structure engages the rib structure of the housing, the anti-rotation of the stationary ring relative to the housing is achieved.
In the present invention, the seal structure extends from both sides of the stationary ring so as to cover the inside of the bearing, the protrusion is provided on at least one of both seal structures, and the sensor It is provided in either one of these seal structures. In this case, the projecting portion of the seal structure is provided at a position separated from the bearing outer side than the base end portion fitted to the stationary wheel.

  According to the present invention, there is provided a railway vehicle bearing device capable of continuously using a bearing for a long period of time by preventing the outer ring from rotating relative to the housing regardless of the magnitude of the creep force. Can be realized.

Hereinafter, a railway vehicle bearing device according to an embodiment of the present invention will be described with reference to the accompanying drawings.
FIGS. 1A and 1B show an example of a railway vehicle bearing device using a tapered roller bearing. The bearing device is an outer ring (stationary ring) 1 that is always kept in a non-rotating state. And an inner ring (rotating wheel) 3 disposed rotatably facing the inner side of the outer ring 1, and a plurality of raceway surfaces 1 s and 3 s formed continuously on the opposing surfaces of the outer ring 1 and the inner ring 3 in the circumferential direction. A plurality of rolling elements (rollers) 5 incorporated so as to be freely rotatable along the outer periphery of the inner ring 1 and 3 and revolving along the outer and inner rings 1 and 3 while holding the rolling elements (rollers) 5 one by one. For example, a cage 11 made of resin is provided.

  In such a bearing device, two inner rings 3 are fitted (attached) to an axle (rotating shaft) 13 of a railway vehicle with the back surfaces of the inner rings 3 abutting against an annular spacer 15. A single (integrated) outer ring 1 is fitted (attached) to a housing H1 constituting a bearing device. In this case, a single annular inner ring raceway surface 3s is formed on the facing surface of each inner ring 3 so as to incline toward the end along the direction away from the spacer 15 side and continue in the circumferential direction. On the other hand, on the opposing surface of the outer ring 1, two annular outer ring raceway surfaces 1s that are inclined along the inner ring raceway surface 3s of each inner ring 3 and are continuous in the circumferential direction are formed.

  Further, on both sides of each inner ring raceway surface 3s, annular flanges 7 and 9 are projected along the raceway surface 3s, and the projecting diameter dimensions thereof are different from each other. Specifically, in each inner ring 3, the flange portion 7 on the spacer 15 side (hereinafter referred to as a small-diameter flange portion 7) is set to a relatively small-diameter protruding dimension. The flange portion 9 on the 15 side (hereinafter referred to as the large-diameter flange portion 9) is set to have a projecting dimension having a relatively larger diameter than the flange portion 7 on the spacer 15 side.

  On both sides of the two inner rings 3 having such a configuration, annular oil draining members 17 and 19 that constitute a rotating wheel together with the inner ring 3 are fitted to a railcar axle (rotating shaft) 13, respectively. The tapered roller bearing is positioned and fixed to the axle 13 by applying the pressing body 21 in the axial direction to the oil draining member 17 on one side thereof (the left side in FIG. 1B) and tightening with the bolt 23. Can do. In this state, when the axle 13 is rotated, while the outer inner rings 1 and 3 are rotated relative to each other (during bearing rotation), a plurality of pieces incorporated together with the cage 11 between the raceway surfaces 1 s and 3 s of the outer inner rings 1 and 3. The rolling elements (rollers) 5 are held and guided by the flanges 7 and 9, and roll along the raceway surfaces 1s and 3s.

  Further, in the above-described bearing device, a predetermined amount of lubricant (for example, oil, grease) is sealed inside the bearing in order to maintain constant lubrication performance and rotational performance during the rotation of the bearing. In this case, in order to prevent the lubricant from leaking to the outside of the bearing and to prevent foreign matter (for example, water, dust) from entering the inside of the bearing, both sides of the outer inner rings 1 and 3 are respectively provided inside the bearing. A sealing mechanism is provided for sealing the shaft from the outside of the bearing.

  As the sealing mechanism, annular seal structures 25a and 25b facing the left oil draining member 17 and the right oil draining member 19 in the middle of FIG. 1B are provided. Each of the seal structures 25a and 25b extends in a ring shape so as to cover the inside of the bearing from both sides of the outer ring (stationary ring) 1 with its base end Pe fitted to the outer ring (stationary ring) 1. Configured. More specifically, one seal structure 25a extends in a ring shape with its base end Pe fitted to the outer ring (stationary ring) 1, and its tip Pt contacts the oil draining member 17. It is positioned and arranged without entering the oil draining member 17. In this case, a narrow passage is formed between the distal end portion Pt of the seal structure 25a and the oil draining member 17, thereby constituting a labyrinth seal that seals the inside of the bearing from the outside of the bearing.

  The other seal structure 25b extends in a ring shape with its base end portion Pe fitted to the outer ring (stationary ring) 1, and its tip end Pt does not contact the oil draining member 19 and It is positioned and placed in a state where it partially enters the oil draining member 19. In this case, the seal structure 25b is used as a seal case, and a sealing member 27 such as a seal, a shield, or a pack seal is interposed between the seal case and the oil draining member 19. Thereby, the oil seal which seals the inside of a bearing from the outside of a bearing is constituted.

  The railway vehicle bearing device of the present embodiment includes a sensor 30 for detecting relative rotation between the outer ring (stationary wheel) 1 and the inner ring (rotating wheel) 3. In this case, the sensor 30 can be arranged at an arbitrary position as long as it can detect the relative rotation between the outer ring (stationary ring) 1 and the inner ring (rotating ring) 3. However, as an example, the sensor 30 is here. Is assumed to be disposed in one seal structure 25a facing the oil draining member 17 on the left side in FIG. 1 (b). Moreover, as a method of attaching the sensor 30 to one seal structure 25a, various methods such as adhesion, fitting, and screwing can be applied. In the drawing, as an example, a configuration in which the sensor 30 is screwed to one seal structure 25a is shown.

  By the way, in the railway vehicle bearing device of the present embodiment, the outer ring 1 fitted (attached) to the housing H1 is relative to the housing H1 when the outer ring (stationary ring) 1 and the inner ring (rotating ring) 3 rotate relative to each other. On the other hand, a structure for preventing rotation (creep) is provided. Hereinafter, this configuration will be specifically described.

  As shown in FIGS. 1A to 1E, in the bearing device of the present embodiment, at least one protrusion F1 protruding toward the housing H1 is provided on the outer periphery of one seal structure 25a. The seal structure 25a is provided as an integral structure. Here, as an example, it is assumed that a plurality (two) of protrusions F1 are provided on the outer periphery of one seal structure 25a along the circumferential direction.

  Further, regarding the amount of protrusion that causes each protrusion F1 to protrude in the direction of the housing H1, when the outer ring 1 rotates (creep) with respect to the housing H1, the protrusion F1 becomes a rib structure R1 (described later). It is preferable to set it to such an extent that it can be engaged (contacted).

  In this case, a method for making each protrusion F1 integrally with the seal structure 25a is, for example, by cutting or pressing when forming the seal structure 25a, so that a part of the outer periphery of the seal structure 25a is formed. The protrusion F1 having a desired size and shape may be integrally formed by projecting. Further, in the configuration in which each protrusion F1 is integrated with the seal structure 25a, the size and shape of each protrusion F1 is, for example, the size and shape of the outer periphery of the seal structure 25a, or the rib structure formed in the housing H1. Since it is set corresponding to the size and shape of the body R1 (described later), there is no particular limitation. In addition, although the protrusion F1 which comprises the cross-sectional rectangular solid shape is shown as an example in drawing, it is not limited to this, For example, various solid shapes, such as a cross-sectional ellipse, a cross-sectional triangle, or a cross-sectional trapezoid, are shown. The protruding portion F1 can be configured.

  Further, the protruding position of each protruding portion F1 on the outer periphery of the seal structure 25a corresponds to, for example, the usage environment and purpose of the railway vehicle bearing device, or the posture and orientation when the housing H1 is mounted on the outer ring 1. Therefore, there is no particular limitation. In the drawing, as an example, each protrusion F1 is positioned along the circumferential direction on the outer periphery of the seal structure 25a in a range where the housing H1 is mounted. In this case, it is preferable that the projecting position of each projecting portion F1 is set so as not to be deviated to one side (eccentric) and symmetrical in the mounting range of the housing H1 (see FIG. 1A). Here, the circumferential length of each protrusion F1 may be set to a size that fits within the mounting range of the housing H1.

  Further, the material of each protrusion F1 that is integrated with the seal structure 25a is the same material as that of the seal structure 25a, and is not particularly limited here, but the material of the seal structure 25a is, for example, a metal material or When a resin material or the like is applied, each protrusion F1 is configured by the metal material or the resin material.

  On the other hand, a rib structure R1 is provided in the housing H1 so as to face each of the protrusions F1 described above. Specifically, the rib structure R1 is opposed to the outer periphery of the seal structure 25a extending between the protrusions F1, and continuously in the circumferential direction over the region between the protrusions F1. Is provided. In this case, the size and shape of the rib structure R1 is such that the rib structure R1 is in direct contact with the seal structure 25a and the protrusions F1 in a state where the housing H1 is mounted on the outer ring 1. It is preferable to set so that a predetermined gap is formed between each other and maintained. In addition, the circumferential length of the rib structure R1 may be set to a dimension that fits between the protrusions F1. The rib structure R1 may be formed as an integral structure with the housing H1, or the rib structure R1 may be formed as a separate structure from the housing H1 and retrofitted to the housing H1. .

  In the protrusion F1 of the seal structure 25a and the rib structure R1 of the housing H1 described above, the creep that tries to rotate the outer ring 1 when the outer ring (stationary ring) 1 and the inner ring (rotating ring) 3 rotate relative to each other. As shown in FIGS. 1C and 1D, when the force is generated, at the portion where the protrusion F1 and the rib structure R1 are engaged, the protrusion F1 faces the rib structure R1 and is flat. It is preferable to form a flat seal-engaging surface Fs and to form a flat rib-engaging surface Rs on the rib structure R1 so as to face the seal-engaging surface Fs. In this case, when the protrusion F1 of the seal structure 25a and the rib structure R1 of the housing H1 are engaged, the seal engagement surface Fs of the protrusion F1 and the rib engagement surface Rs of the rib structure R1 are: They are in contact with each other at a predetermined angle θ (FIG. 1 (d)). Here, the contact angle θ is set so that the rib engagement surface Rs contacts the seal engagement surface Fs in the vicinity of the base of the protrusion F1. Thereby, the seal engagement surface Fs and the rib engagement surface Rs can be brought into surface contact with each other. As a result, when a creep force for rotating the outer ring 1 is generated, a cause of damage such as elastic deformation or plastic deformation due to conformance is generated in a portion where the protrusion F1 and the rib structure R1 are engaged. It can be prevented in advance. The contact angle θ is arbitrarily set according to, for example, the use environment and purpose of the bearing device, or the shape and size of the portion where the protrusion F1 and the rib structure R1 are engaged. Although the numerical value is not particularly limited here, θ ≦ 1 ° may be set as an example.

  As described above, according to the present embodiment, the protrusion F1 is integrally formed on the outer periphery of one seal structure 25a in which the base end Pe is fitted to the outer ring (stationary ring) 1, and the housing H1 is attached to the outer ring 1. In this state, when a creep force is generated to rotate the outer ring 1 during the relative rotation of the outer inner rings 1 and 3, the protrusion F1 is engaged with the rib structure R1 of the housing H1, It is possible to prevent the outer ring 1 from rotating relative to the housing H1.

  More specifically, as shown in FIG. 1 (c), when the outer ring 1 and 3 rotate relative to each other, the outer ring 1 rotates (creep) in one direction T with respect to the housing H1. When the body 25a also rotates in the same direction, as shown in FIG. 1 (d), the projecting portion F1 of the seal structure 25a abuts against the rib structure R1 of the housing H1 and no longer rotates. On the contrary, when the outer ring 1 rotates (creep) in the other direction (the direction opposite to the arrow T), the protruding portion F1 on the opposite side of the rib structure R1 contacts the rib structure R1. No more turns. Thereby, rotation of the outer ring 1 in the circumferential direction relative to the housing H1 can be prevented during rotation of the bearing (forward and reverse rotation). As a result, for example, an unexpected situation in which the sensor 30 disposed in the seal structure 25a collides with the housing H1 or the cable connected to the sensor 30 is disconnected can be avoided. Can do.

  In addition, according to the present embodiment, the flat seal engagement surface Fs is formed in the protrusion F1, and the flat rib engagement surface Rs is formed in the rib structure R1, so that the protrusion F1 When the rib structure R1 is engaged, the seal engagement surface Fs and the rib engagement surface Rs can be brought into surface contact with each other at the predetermined contact angle θ described above. In this case, the contact pressure (contact load) at the time of engagement between the protrusion F1 and the rib structure R1 is distributed over the entire surface of the seal engagement surface Fs and the rib engagement surface Rs that are in surface contact with each other. Does not act locally (does not work excessively).

  In other words, the creep force that tries to rotate the outer ring 1 first engages the protrusion F1 and the rib structure R1 in a state where the protrusion F1 and the rib structure R1 are engaged. It is transmitted (propagated) to the part. Then, the protrusion F1 and the rib structure R1 are engaged with each other by a contact pressure (contact load) corresponding to the magnitude of the transmitted (propagated) creep force. At this time, since the seal engagement surface Fs and the rib engagement surface Rs are in surface contact with each other as described above, it is possible to cause the engagement portion to slip. For this reason, excessive load (for example, frictional force) does not act on the protrusion F1.

  Accordingly, even when the load on the engaging portion is excessive, it is possible to reliably avoid the situation where the protruding portion F1 is damaged. Therefore, the seal structure 25a in which the protruding portion F1 is integrated is provided. It can continue to function stably as a sealing mechanism over a long period of time. In this case, it is possible to reliably prevent foreign matter (e.g., broken pieces of the engaging portion, dust) from entering the bearing or leakage of the lubricant sealed inside the bearing to the outside. . As a result, for example, a situation such as bearing locking or seizure can be avoided in advance, so that the bearing device can be continuously used over a long period of time.

  Further, according to the present embodiment, a plurality of (two in the drawing) protrusions F1 are provided on the outer periphery of the seal structure 25a, and the rib structure R1 is formed in the housing H1 between these protrusions F1. Thus, when the housing H1 is mounted on the outer ring 1, the outer ring 1 can be easily and accurately positioned with respect to the housing H1 by simply disposing each protrusion F1 on both sides of the rib structure R1. . Thereby, the sensor 30 can be accurately and quickly positioned at a preset position (for example, arrangement, posture, etc.).

  Here, in the present embodiment, it is preferable that the protruding portion F1 of the seal structure 25a is provided at a position separated from the base end portion Pe fitted to the outer ring (stationary ring) 1 toward the outside of the bearing. More specifically, as shown in FIG. 1 (e), the seal structure 25a is relatively thicker at the portion closer to the outside of the bearing than the base end portion Pe along the circumferential direction than the other portions. It is configured to have an annular shape. In this case, the strength (rigidity) of the annular portion is relatively higher than other portions. For this reason, even when the above-described excessive load is applied to the portion where the protrusion F1 and the rib structure R1 are engaged by integrating the protrusion F1 with the annular portion, the load It is possible to maintain high durability against. As a result, the seal structure 25a in which the protrusion F1 is integrally structured can be stably functioned as a sealing mechanism.

  Further, in the present embodiment, as shown in FIGS. 1 (e) and 2, it is preferable that the seal structure 25a is formed with a seal end face Ps on the bearing outer side. In this case, when the base end portion Pe of the seal structure 25a is fitted to the outer ring (stationary ring) 1, the seal end surface Ps faces the rib structure R1 of the housing H1 in parallel with a slight gap therebetween ( What is necessary is just to form in the site | part which directly faces). Here, as an example, the seal end surface Ps is formed as an annular surface continuous along the circumferential direction on the bearing outer side of the base end portion Pe of the seal structure 25a. In this case, it is preferable to set the chamfer of the outer shape portion of the seal end surface Ps as small as possible. The chamfer dimension (C) is arbitrarily set in accordance with, for example, the use environment and purpose of the bearing device, or the shape and size of the seal end face Ps. The chamfer dimension (C) may be set to 1 mm or less. Thus, when the base end Pe is fitted to the outer ring 1, the seal end face Ps can be directly opposed to the rib structure R1 with a slight gap therebetween. As a result, it is possible to prevent (fail-safe) the dropout of the seal structure 25a from the outer ring 1 (extraction toward the outside of the bearing).

The present invention is not limited to the above-described embodiment, and the following modifications are also included in the technical scope of the present invention, and the same effect can be realized.
In the embodiment described above, it is assumed that a plurality of (two in the drawing) protrusions F1 are provided on the outer periphery of one seal structure 25a, but as a modified example, as shown in FIG. A single (one) protruding portion F1 protruding toward the housing H1 may be provided on the outer periphery of the seal structure 25a. Note that the size, shape, and material of the protrusion F1 may be the same as those in the above-described embodiment.

  In this case, the projecting position of the projecting portion F1 is preferably set at the center (center) within the range where the housing H1 is mounted. Correspondingly, the rib structure R1 is in a state in which the rib structure R1 is not in direct contact with the seal structure 25a and the projecting portion F1 in a state where the housing H1 is mounted on the outer ring 1. It is preferable to set so that a predetermined gap is formed between each other and maintained.

  Specifically, since the protrusion F1 is positioned at the center (center) of the mounting range of the housing H1, the above-described protrusion is provided at the center (center) of the rib structure R1. A concave portion Rg capable of accommodating F1 is formed so as to be recessed from other portions. In this case, the concave portion Rg is formed to be depressed so that it does not directly (directly) contact the protruding portion F1 when the housing H1 is mounted on the outer ring 1. Moreover, since the magnitude | size and shape of the recessed part Rg are set corresponding to the magnitude | size and shape of the protrusion part F1 accommodated here, it does not specifically limit. Even in the case of such a modification, as in the above-described embodiment, in the portion where the protrusion F1 and the rib structure R1 are engaged, on both sides of the protrusion F1, the rib structure R1 is opposed. It is preferable to form the flat seal engagement surface Fs and to form the flat rib engagement surface Rs on the rib structure R1 so as to face the seal engagement surface Fs.

  Further, in the above-described embodiment, the description has been made assuming that the projecting portion F1 is provided as an integral structure on one seal structure 25a. However, the present invention is not limited to this, and the other seal structure is provided. A protrusion (not shown) may be provided integrally on the body 25b, or a protrusion may be provided integrally on both the seal structures 25a and 25b. In this case, the configuration and the method for integrating the protrusions with the other seal structure 25b are the same as those in the above-described embodiment, and thus the description thereof is omitted. Here, when a protrusion is provided on the other seal structure 25b, a rib structure R2 (see FIG. 1 (b)) that has the same configuration as the rib structure R1 described above is opposed to the protrusion. ) May be formed in the housing H1.

  Further, in the above-described embodiment and the first and second modified examples, the description has been made assuming a tapered roller bearing, but instead of this, a railway using a cylindrical roller bearing to which a cylindrical roller is applied as the rolling element 5. The same effect can be realized as a vehicle bearing device.

  Further, in the above-described embodiment and its modified examples, the case where one or two protrusions F1 are provided on the outer periphery of the seal structure 25a, 25b has been described, but the use environment and purpose of the bearing device are illustrated. Depending on, three or more protrusions F1 may be provided.

(a) is a plan view of an exterior configuration of a railway vehicle bearing device according to an embodiment of the present invention as viewed from the sensor side, and (b) is a railway vehicle bearing device shown in FIG. FIG. 4C is a cross-sectional view schematically showing the internal configuration of FIG. 1, FIG. 5C is an enlarged view of the configuration surrounded by the symbol Wc in FIG. 4A, and FIG. The figure which shows the state which the protrusion part of the seal | sticker structure engaged with the rib structure of the housing in the part enclosed by Wc, (e) is the structure of the part enclosed by the code | symbol Wc of the same figure (a). The figure which cuts and shows in radial direction. (a) is a plan view showing a partially enlarged configuration of the seal structure, (b) is a cross-sectional view taken along line XX of FIG. (a), and (c) is the same figure (a). Sectional drawing which follows the YY line | wire, (d) is a figure which expands and shows the structure of the part enclosed by the code | symbol Wd of FIG.1 (b). The figure which shows the structure of the characteristic part of the bearing apparatus for railway vehicles which concerns on the modification of this invention.

Explanation of symbols

1 Outer ring (stationary ring)
3 Inner ring (rotating wheel)
25a Seal structure 30 Sensor F1 Projection H1 Housing Pe Base end R1 of seal structure Rib structure

Claims (3)

A rotating wheel mounted on a rotating shaft of a railway vehicle, a stationary wheel arranged opposite to the rotating wheel and mounted with a housing of a bearing device, and a bearing inside constituted by the rotating wheel and the stationary wheel are externally provided from the bearing. A railcar bearing device comprising a sealing mechanism for sealing and a sensor for detecting relative rotation between a rotating wheel and a stationary wheel,
The sealing mechanism has an annular seal structure extending so as to cover the inside of the bearing in a state where the base end portion is fitted to the stationary ring, and the outer periphery of the seal structure is directed toward the housing. And at least one projecting portion that projects in a unitary structure with the seal structure,
In a state where the housing is mounted on the stationary wheel, when a force for rotating the stationary wheel is generated during relative rotation between the rotating wheel and the stationary wheel, the protruding portion of the seal structure engages with the rib structure of the housing. This prevents the stationary wheel from rotating with respect to the housing. The seal structure extends from both sides of the stationary ring so as to cover the inside of the bearing, and the protrusion is provided on at least one of both seal structures,
The bearing device for a railway vehicle according to claim 1, wherein the sensor is provided in any one of both seal structures.   The railcar bearing device according to claim 1, wherein the projecting portion of the seal structure is provided at a position spaced apart from the base end portion fitted to the stationary wheel toward the outside of the bearing. .

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