JP2007120695A - Bearing device for vehicle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve abrasion resistance of a rotating wheel, and to provide a low-cost bearing device for a vehicle that is superior in operability to attach to an axle. <P>SOLUTION: The bearing device for the vehicle for rotatably pivoting the axle S of a variety of vehicles is provided with a rolling bearing A with a static wheel 4 and rotating wheels 2 (2a, 2b) provided relatively rotatably to face each other via a plurality of rolling elements 6a, 6b and ring-shape positioning members F, P for positioning the rotating wheels in the axial direction. The positioning members are provided so as to contact with end surfaces 2e, 2f of the rotating wheels facing the end surfaces F1, P1 of the positioning members from an axial direction and to be capable of rotating with the rotating wheel, and at least one of the end surfaces of the positioning members and the end surfaces of the rotating wheel facing the end surfaces is integrally provided with a lubrication layer J, formed by spray coating a nonmetallic material. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a bearing device used for, for example, an axle of a railway vehicle, and more particularly to an improvement of a vehicle bearing device provided with a sealing structure effective for preventing foreign matter from entering a bearing.

  A bearing device for a railway vehicle has a structure as shown in FIGS. 3A and 3B, for example, and is a bearing (a double row tapered roller that is externally fitted to the axle S and supports the axle S). Bearing) A, an annular rear lid F for axially positioning a rotating wheel (inner ring) 2 (described later) of bearing A, and the lubricant enclosed in bearing A are prevented from leaking to the outside. And an annular oil drain P for the purpose.

  The bearing A includes a rotating wheel (inner ring) 2 connected to a wheel (not shown) and rotating together with the wheel, and a stationary wheel (outer ring) fixed to a vehicle housing (not shown) and maintained in a non-rotating state at all times. 4, a plurality of rolling elements (rollers) 6 a and 6 b incorporated between a rotating wheel (inner ring) 2 and a stationary wheel (outer ring) 4 in a double row (for example, two rows). (Rollers) 6a and 6b, and a cage 12 for holding each one rotatably. In the configuration shown in FIG. 3 (a), the inner ring 2 is composed of a first inner ring 2a and a second inner ring 2b, and a first raceway surface 8a is formed on the first inner ring 2a. A second raceway surface 8b is formed on each second inner ring 2b. An annular inner ring spacer 14 is interposed between the first inner ring 2a and the second inner ring 2b. In this case, the end surface 2c of the first inner ring 2a and the end surface 14a of the inner ring spacer 14 are in contact with each other, and the end surface 2d of the second inner ring 2b and the end surface 14b of the inner ring spacer 14 are in contact with each other.

  Further, the rear lid F and the oil drainer P each have a hollow cylindrical shape, and are fitted onto the axle S. In this case, the end surface 2e of the first inner ring 2a and the end surface F1 of the rear lid F are in contact with each other, and the end surface 2f of the second inner ring 2b and the end surface P1 of the oil draining P are in contact with each other. As described above, the bearing A has the inner ring 2 (2a, 2b) in contact with the inner ring spacer 14, the rear lid F and the oil drain P, and the outer ring 4 is fixed to a vehicle housing (not shown). Positioned along the direction. In addition, the inner ring | wheel 2 (2a, 2b) and the outer ring | wheel 4 are formed with bearing steel as an example, and the back cover F and the oil drainer P are formed with normalized carbon steel as an example.

  Further, the bearing A has contact portions (end surfaces 2e, F1) between the first inner ring 2a and the rear lid F, and contact portions (end surfaces 2f, P1) between the second inner ring 2b and the oil draining P. A sealing case 16 is provided so as to cover a cylindrical shape having a stepped shape (for example, three steps) in cross section. In this case, one end side (large diameter side) of the seal case 16 is fitted into the outer ring 4. An oil seal 18 for sealing the bearing A is interposed between the seal case 16 and the rear lid F and between the seal case 16 and the oil drain P. As the oil seal 18, an outer diameter portion 18 a is fitted in the seal case 16, and an inner diameter portion 18 b is slidably in contact with the rear cover F and the outer peripheral surfaces F 2 and P 2 of the oil drain P (for example, Rubber or synthetic resin seals are applied. By providing the seal case 16 and the oil seal 18 in this way, foreign matters (for example, water and dust) enter the bearing from the outside of the bearing and a lubricant (for example, lubricating oil and grease) from the inside of the bearing to the outside of the bearing. Leakage can be prevented.

  By the way, when the railway vehicle travels, a large load is applied to the axle S, which causes a bending moment to be applied to the axle S, and the axle S may be bent. Normally, the inner ring 2 (2a, 2b), the back cover F, and the oil drain P of the bearing A are made of metal as described above. When the axle S is rotated in a bent state, the inner rings 2a, 2b and the back cover F are rotated. And end face 2e, 2f of inner rings 2a, 2b and end face F1, P1 of end face F, and end face F, P1 may wear and generate metal powder (fretting). .

  In this case, the metal powder caused by fretting moves radially between the contact surfaces due to centrifugal force (in the direction from the inner ring 2 toward the outer ring 4) and enters the bearing A, and the lubricant enclosed in the bearing A It will be mixed. As a result, for example, the lubrication performance of the lubricant is deteriorated, or the metal powder enters between the rolling elements (rollers) 6a, 6b and the inner and outer rings, so that the surface of the rolling elements (rollers) 6a, 6b The raceway surfaces 8a, 8b, 10a, 10b may be damaged, and it may be difficult to continuously use the bearing A with a certain performance over a long period of time, such as reducing the bearing life.

  As a method for suppressing the occurrence of such fretting, for example, there is a method in which a dissimilar material plate (not shown) is interposed between the end surface 2e of the inner ring 2 (first inner ring 2a) and the end surface F1 of the rear lid F. Yes (see Patent Document 1). In such a method, a dissimilar material plate is interposed between the end surface 2e of the inner ring 2 (first inner ring 2a) and the end surface F1 of the rear lid F so that they do not come into direct contact with each other. It avoids wearing and suppresses the occurrence of fretting and the accompanying metal powder. The dissimilar material plate is an annular and flat part made of a material different from the inner ring 2 (first inner ring 2a), the rear lid F, and the like.

However, since the dissimilar material plate is a separate part configured to be separate from the inner ring 2 and the back cover F, the number of parts increases and the number of assembly steps increases. For example, the back cover F (end face There is a risk of inducing work mistakes such as forgetting to attach to F1). Further, since the dissimilar material plate is a separate part from the inner ring 2 (2a) and the rear cover F, when the bearing device (the inner ring 2 (2a), the rear cover F) is externally fitted (for example, press-fitted) to the axle S, for example, There is also a possibility that the rear lid F (end surface F1) may come off. In this case, the work must be performed again, resulting in extra work costs.
JP 2003-49856 A

  The present invention has been made to solve such a problem, and an object of the present invention is to improve the wear resistance of a rotating wheel and to provide a low-cost vehicle bearing device that is excellent in workability on an axle. It is to provide.

  In order to achieve such an object, a vehicle bearing device according to the present invention includes a stationary wheel that rotatably supports axles of various vehicles and is opposed to each other so as to be relatively rotatable via a plurality of rolling elements. A rolling bearing having a rotating wheel and an annular positioning member for positioning the rotating wheel in the axial direction are provided. In such a configuration, the positioning member is in contact with the end surface of the rotating wheel opposed to the end surface in the axial direction and is rotatably arranged with the rotating wheel, and is opposed to the end surface of the positioning member and the end surface. A lubricating layer formed by spraying a nonmetallic material is integrally provided on at least one of the end faces of the rotating wheel. In this case, as the positioning member, a rear lid and an oil drainer are applied.

  ADVANTAGE OF THE INVENTION According to this invention, while improving the abrasion resistance of a rotating wheel, the low-cost vehicle bearing apparatus excellent in the workability | operativity to the axle can be provided.

  Hereinafter, a vehicle bearing device according to an embodiment of the present invention will be described with reference to the accompanying drawings. Note that the bearing device of the present invention can be applied to various vehicles such as railroads and automobiles, but here, a bearing device for railcars will be described as an example.

1A and 1B show a railway vehicle bearing device according to an embodiment of the present invention.
Such a bearing device rotatably supports an axle S of a railway vehicle, and a stationary wheel (outer ring) 4 and a rotating wheel (inner ring) that are arranged so as to be relatively rotatable via a plurality of rolling elements (rollers) 6a and 6b. ) 2 and a ring-shaped positioning member for positioning the inner ring 2 in the axial direction. Here, as the positioning member, a rear cover F and an oil drainer P provided on both sides in the axial direction of the rolling bearing A are applied, and the rear cover F is a base end side of the axle S (for example, a vehicle suspension device). On the side (not shown) (the right side of FIG. 1A)), the oil drain P is fitted to the front end side (for example, the wheel (not shown) side (FIG. 1A) of the axle S. ) Is fitted on the outer peripheral surface small-diameter portion S3. The axle S is formed with a relatively large diameter outer peripheral surface portion S2 on the right side of FIG. 1A with the outer peripheral surface step portion S1 as a boundary, and a relatively small diameter outer peripheral surface on the left side of FIG. A small diameter portion S3 is formed. In this case, the front end of the axle S is arranged so that the inner ring 2, the rear lid F and the oil drain P of the bearing A of the bearing device are sandwiched between the outer peripheral surface step S1 of the axle S and the nut 20. From the side, it is fixed (unscrewed) with a bolt 24 through a rotation prevention ring 22.

  In the configuration shown in FIG. 1A, an outer ring integrated double row (two rows) type tapered roller bearing is applied to the rolling bearing A. In this case, in the bearing A, the inner ring 2 rotates together with the axle S connected to the wheels (not shown), whereas the outer ring 4 is fixed to the vehicle housing (not shown) and is always kept in a non-rotating state. Yes. In the bearing A, the inner ring 2 is composed of a first inner ring 2a and a second inner ring 2b. The first inner ring 2a has a first raceway surface 8a, and the second inner ring 2b has A second raceway surface 8b is formed, and the outer ring 4 is formed with double-row (two rows) raceway surfaces 10a and 10b facing the first and second raceway surfaces 8a and 8b. A plurality of rollers 6a and 6b are rotatably incorporated between the raceway surfaces 8a and 10a and between the raceway surfaces 8b and 10b of the inner and outer rings, and each roller 6a and 6b is rotatable one by one. Is held by a cage 12.

  An annular inner ring spacer 14 is interposed between the first inner ring 2a and the second inner ring 2b. In this case, the end surface 2c of the first inner ring 2a and the end surface 14a of the inner ring spacer 14 are in contact with each other, and the end surface 2d of the second inner ring 2b and the end surface 14b of the inner ring spacer 14 are in contact with each other. Instead of providing the inner ring spacer 14, the first inner ring 2 a and the second inner ring 2 b may be arranged so that the end faces 2 c and 2 d facing each other directly contact each other. Further, the inner ring 2 may be an integrated inner ring 2 in which the first inner ring 2a and the second inner ring 2b are not divided into a single piece. Further, the outer ring 4 may be divided, and in this case, an outer ring spacer (not shown) can be selectively provided.

  In this case, an action line (not shown) orthogonal to the rotation axis of the roller 6a and an action line (not shown) orthogonal to the rotation axis of the roller 6b are formed outside the outer ring 4 (for example, a vehicle housing (not shown)). Cross at the side). This constitutes a rear combination (DB) bearing. In such a configuration, for example, the force acting on the wheel of the railway vehicle is transmitted from the wheel to the vehicle body (for example, the housing of the vehicle) through the bearing device (bearing A). ) Is subjected to various loads (radial load, axial load, moment load, etc.). However, since the bearing A is a back-to-back (DB) bearing, high rigidity can be maintained against various loads (radial load, axial load, moment load, etc.).

Further, in the bearing A, the end surface 2e of the first inner ring 2a and the end surface F1 of the rear lid F abut each other, and the end surface 2f of the second inner ring 2b and the end surface P1 of the oil draining P abut each other. A seal case 16 is provided so as to cover the portion and form a cylindrical shape having a stepped shape in cross section (for example, three steps). In this case, as an example, one end side (large diameter side) of the seal case 16 is fitted into the outer ring 4, and the other end side (small diameter side) extends in the direction of the rear lid F and the oil draining P, and the extension The end is positioned in a non-contact state with the rear lid F and the oil drainer P. An oil seal 18 for sealing the bearing A is interposed between the seal case 16 and the rear lid F and between the seal case 16 and the oil drain P. As the oil seal 18, an outer diameter portion 18 a is fitted in the seal case 16, and an inner diameter portion 18 b is slidably in contact with the rear cover F and the outer peripheral surfaces F 2 and P 2 of the oil drain P (for example, Rubber or synthetic resin seals are applied.
By providing the seal case 16 and the oil seal 18 in this way, foreign matters (for example, water and dust) enter the bearing from the outside of the bearing and a lubricant (for example, lubricating oil and grease) from the inside of the bearing to the outside of the bearing. Leakage can be prevented. Note that one end side (large diameter side) of the seal case 16 may be externally fitted to the outer ring 4, and the oil seal 18 may be a non-contact type seal or shield.

  In the present embodiment, the rear lid F and the oil drainer P each have a hollow cylindrical shape, and are externally fitted to the axle S so as to be rotatable together with the inner ring 2 (2a, 2b) of the bearing A. In the configuration shown in FIG. 1A, the rear lid F has a step-like (two-step) cylindrical shape, and its large-diameter side inner peripheral surface F4 abuts on the outer peripheral surface large-diameter portion S2 of the axle S. The inner peripheral intermediate portion F6 connecting the large-diameter side inner peripheral surface F4 and the small-diameter side inner peripheral surface F5 abuts on the outer peripheral surface stepped portion S1 of the axle S, and the small-diameter inner peripheral surface F5 is connected to the axle S. It is externally fitted so as to face the outer peripheral surface small-diameter portion S3. In this case, the inner peripheral intermediate portion F6 of the rear lid F is formed in a convex curved surface shape that is continuous along the outer peripheral surface step portion S1 of the axle S. In this state, the rear cover F has a small-diameter outer peripheral surface F2 that is in sliding contact with an inner diameter portion (for example, a lip portion (not shown)) 18b of the oil seal 18 and a large-diameter outer peripheral surface F3 that is a seal case. 16 is partially opposed to the inner peripheral portion 16a. Further, the rear cover F has an end surface F1 on one end side (for example, a wheel (not shown) side (left side in FIG. 1A)) in an axial direction on an end surface 2e of the opposed inner ring 2 (first inner ring 2a). (For example, the vehicle abuts from the suspension (not shown) side (the right side of FIG. 1A)).

  On the other hand, the oil drain P is annularly formed on a main body Pm formed in a hollow cylindrical shape and an outer peripheral surface P2 on one end side of the main body Pm (for example, on the wheel side (left side in FIG. 1A)). In addition, the flange portion Pf is provided in a series, and the inner peripheral surface P3 of the main body Pm is externally fitted so as to contact the outer peripheral surface small diameter portion S3 of the axle shaft S. In this state, the oil drain P has an outer peripheral surface P2 of the main body Pm that is in sliding contact with an inner diameter portion (for example, a lip portion of the seal) 18b of the oil seal 18 and a flange portion Pf of the inner peripheral portion 16a of the seal case 16. And partially facing. In addition, the end face P1 on one end side (for example, the vehicle suspension device side (the right side in FIG. 1A)) of the oil drainer P is axially directed to the end face 2f of the opposing inner ring 2 (second inner ring 2b) ( For example, it is in contact with the wheel side (left side in FIG. 1A)) and the end face P4 on the other end side (for example, wheel side (left side in FIG. 1A)) is in contact with the nut 20. .

  In this embodiment, at least one of the end faces F1, P1 of the positioning member (rear cover F and oil drainer P) and the end faces 2e, 2f of the inner ring 2 (2a, 2b) facing the end faces F1, P1 is non-metallic. A lubricating layer J formed by spraying the material is integrally formed. 1 (a) and 1 (b), the end face F1 (inner ring 2 (first inner ring) on one end side of the rear lid F (for example, the wheel side (left side of FIGS. 1 (a) and 1 (b))) is provided. A lubricating layer J formed by spraying a non-metallic material (for example, resin (rubber) or plastic) is provided integrally with the rear lid F on the surface 2a facing the end surface 2e). . In this case, the rear cover F has a lubricating layer J formed on the end face F1 in the axial direction (for example, the vehicle suspension side (FIG. 1 (a)) on the end face 2e of the opposed inner ring 2 (first inner ring 2a). ), the right side of (b))).

The lubrication layer J can be integrally formed with the back cover F by coating (coating) the end face F1 of the back cover F with a non-metallic material (for example, resin (rubber) or plastic). As an example of the forming method, the coating is sprayed, that is, a non-metallic coating material (for example, resin (rubber) or plastic) is melted or softened by heating to be accelerated into fine particles, and is applied to the end face F1 of the back cover F. The particles can be formed by solidifying and depositing flattened particles on the end face F1 by jetting and colliding. In the configuration shown in FIGS. 1A and 1B, the lubricating layer J is formed only on the end face F1 of the rear lid F. In addition to this, for example, the inner circumference on the large diameter side of the rear lid F is provided. You may form in surface F4 (contact surface with the outer peripheral surface large diameter part S2 of the axle shaft S) and inner peripheral intermediate part F6 (contact surface with the outer peripheral surface level | step-difference part S1 of the axle shaft S), respectively. In this case, a coating (coating) of a non-metallic material (for example, resin (rubber) or plastic) may be formed on the large-diameter side inner peripheral surface F4 and the inner peripheral intermediate portion F6. Further, the lubricating layer J may be formed on the entire surface of the rear lid F.
In addition, as a heat source at the time of heating coating material, since arbitrary heat sources, such as a gas type heater and an electric heater, can be used, it does not specifically limit here.

According to such a configuration, the rear lid F (end surface F1) is in contact with the inner ring 2 (end surface 2e of the first inner ring 2a) via the lubricating layer J. In this case, the rear lid F and the inner ring 2 (first inner ring 2a) rotate smoothly without the contact portions (end surfaces F1, 2e) thereof being rubbed by the lubricating layer J. As a result, fretting does not occur on the end surface 2e of the inner ring 2 (first inner ring 2a), and metal powder associated therewith does not occur. Therefore, for example, fretting metal powder is mixed in the lubricant and the lubrication performance of the lubricant is deteriorated, or the metal powder enters between the rolling elements (rollers) 6a, 6b and the inner and outer rings, thereby causing rolling. The surfaces of the moving bodies (rollers) 6a, 6b and the raceway surfaces 8a, 8b, 10a, 10b are not damaged and the bearing life is not reduced. Thus, by providing the lubricating layer J, the wear resistance of the inner ring 2 (the end surface 2e of the first inner ring 2a) can be improved.
Thereby, a bearing apparatus (bearing A) can be continuously used with a fixed performance over a long period of time.

  Further, since the lubricating layer J is formed integrally with the back cover F, the above-described conventional dissimilar material plate is made up of the end surface 2e of the inner ring 2 (first inner ring 2a) and the end surface F1 of the back cover F. The number of parts does not increase and the number of assembly steps does not increase as in the case of interposing them. For this reason, when the bearing device (the inner ring 2 (2a), the rear lid F) is externally fitted (for example, press-fitted) to the axle S, the work becomes easy, and the mounting workability (working efficiency) can be remarkably improved. it can. Further, the number of parts can be maintained as they are, and the mounting workability (working efficiency) can be greatly improved, so that the bearing device can be manufactured at low cost.

Here, the wear resistance of the bearing device (the inner ring 2 of the bearing A) according to the present embodiment was tested and verified. The test contents and test results will be described below.
In this test, a radial load (Fr) and an axial load (Fa) are applied to the bearing device (bearing A (inner ring 2), rear lid F and oil drain P) on the axle S in a state where the bearing device is externally fitted. ), The axle S and the bearing device (bearing A (inner ring 2), rear lid F and oil drainer P) are rotated at a predetermined speed (N) for a predetermined time, and the inner ring 2 (first The wear resistance of the bearing device (the inner ring 2 of the bearing A) was verified by comparing the state of the end surface 2e) of the inner ring 2a) and the state of the rear lid F (end surface F1) with the state before the test.

  Specifically, as shown in FIGS. 2 (a) and 2 (b), the bearing device according to the present embodiment has a radial load (Fr) of 5820 (kgf) and an axial load (Fa) of 1746 (kgf). The axle S and the bearing device were operated at a speed of 954 revolutions per minute (corresponding to N = 954 (rpm) and 140 km / h (140 km / h)) for about 400 hours. In this case, the basic operation pattern of the axle shaft S and the bearing device is assumed to be normal rotation, reverse rotation, and stop, and the test is started (stopped) from normal rotation (acceleration 1 minute, steady rotation (N = 954 (rpm)). ) 3 hours, decelerated rotation 1 minute), maintain the stopped state for 30 minutes, reverse rotation (acceleration rotation 1 minute, steady rotation (N = 954 (rpm)) 3 hours, deceleration rotation 1 minute). It takes about 6.5 hours (pattern 1) from the start of the test to here. After the operation of pattern 1 is completed, the stopped state is maintained for 30 minutes, the operation of pattern 1 is performed again, and the stopped state is maintained for 6 hours. From the start of the test to this point, it takes about 20 hours (Pattern 2 (Pattern 1, Stop, Pattern 1, Stop)). Then, the operation of pattern 2 was set as one cycle, and this was repeated 20 cycles (see FIG. 2 (a)).

In addition, the basic pattern of the axial load applied to the bearing device is based on a load in one direction with respect to the axial direction (positive load), a load in the opposite direction (reverse load), and a state in which no load is applied (no load state). From the test start state (no load state), a positive load (Fa = 1746 (kgf)) is applied for 5 seconds, the no load state is maintained for 25 seconds, and the reverse load (Fa = 1746 (kgf)) is applied. After acting for 5 seconds, the no-load state is again maintained for 25 seconds. This was defined as one cycle, and the cycle was repeated during the test (see FIG. 2B).
During the test, the bearing device was cooled (air-cooled) by applying a wind of 7 meters / second (7 m / sec) to the bearing device. In addition, the rear lid F was resin-coated by spraying PEEK (polyetheretherketone) resin on the end face F1 (the lubricating layer J was formed).

As a result, no fretting was observed on the end surface 2e of the inner ring 2 (first inner ring 2a) after the test. Further, when the bus bar shape of the end surface 2e of the inner ring 2 (first inner ring 2a) and the bus bar shape of the end surface F1 (lubricating layer J) of the back cover F were enlarged and observed, both end surfaces 2e, F1 before the test were observed. It was confirmed that there was almost no change from the shape of the bus.
As described above, according to the bearing device according to the present embodiment, it was verified by the above-described test that excellent wear resistance (for example, wear resistance of the inner ring 2 of the bearing A) can be exhibited.

In the above-described embodiment, the lubricating layer J is formed on the end surface F1 of the rear lid F (the surface facing the end surface 2e of the inner ring 2 (first inner ring 2a)), but the inner ring 2 (first inner ring 2a). ) End surface 2e (a surface facing the end surface F1 of the back cover F), or may be formed on both end surfaces F1, 2e. Further, the lubricating layer J has an end face P1 of the oil drain P (a face facing the end face 2f of the inner ring 2 (second inner ring 2b)) or an end face 2f of the inner ring 2 (second inner ring 2b) (end face of the oil drain P). May be formed on the opposite surface P1, or may be formed on both end faces P1 and 2f. Further, they may be formed on all of these end faces F1, P1, 2e, 2f, respectively. The lubricating layer J may be formed on the entire surface of the oil drain P and on the entire surface of the inner ring 2 (first inner ring 2a and second inner ring 2b). Furthermore, the lubricating layer J may be formed on the end surfaces 14a, 14b of the inner ring spacer 14 or the entire surface of the inner ring spacer 14.
In this case, the lubricating layer J is coated (coated) with a nonmetallic material (for example, resin (rubber) or plastic) on the surfaces of the oil drain P, the inner ring 2 and the inner ring spacer 14 in the same manner as in the above-described embodiment. It may be formed by doing so.

  In the embodiment described above, the materials of the inner ring 2 (2a, 2b), the outer ring 4, the rear lid F, and the oil drainer P are not particularly mentioned, but they can be formed using arbitrary materials. it can. For example, the inner ring 2 (2a, 2b) and the outer ring 4 may be formed of bearing steel, and the rear lid F and the oil drain P may be formed of normalized carbon steel. In the above-described embodiment, the case where the rollers 6a and 6b are applied as the rolling elements of the bearing A has been described. However, the rolling elements may be balls.

(a) is sectional drawing which shows the structural example of the bearing apparatus for railway vehicles which concerns on one Embodiment of this invention, (b) is a principal part expanded sectional view of the figure (a). (a), (b) is a figure for demonstrating the test content about the abrasion resistance of the bearing apparatus for railway vehicles which concerns on one Embodiment of this invention. (a) is sectional drawing which shows the structural example of the conventional rolling stock bearing apparatus, (b) is a principal part expanded sectional view of the figure (a).

Explanation of symbols

2 (2a, 2b) Rotating wheel (inner ring)
2e, 2f Inner ring end face 4 Stationary ring (outer ring)
6a, 6b Rolling elements (rollers)
A Rolling bearing F Positioning member (rear cover)
F1 Rear cover end face J Lubrication layer P Positioning member (oil drain)
P1 Oil drain end face S Axle

Claims (2)

A bearing device for a vehicle that rotatably supports an axle of various vehicles,
A rolling bearing having a stationary wheel and a rotating wheel which are opposed to each other via a plurality of rolling elements, and an annular positioning member for positioning the rotating wheel in an axial direction;
The positioning member abuts the end surface of the rotating wheel facing the end surface in the axial direction and is rotatably disposed with the rotating wheel, and at least of the end surface of the positioning member and the end surface of the rotating wheel facing the end surface. On one side, a vehicle bearing device is characterized in that a lubricating layer formed by spraying a nonmetallic material is integrally formed. The vehicle bearing device according to claim 1, wherein the positioning member is a rear lid and an oil drainer.

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