JP5361578B2 - Bearing device for rotating electric machine for railway vehicle - Google Patents

Description

  The present invention relates to a bearing device for a rotating electrical machine for a railway vehicle, and more particularly to a bearing device for a rotating electrical machine for a railway vehicle that can supply lubricating oil without hindrance during a rotation test of the rotating electrical machine alone.

  In recent years, there is a growing need for mass transportation and speeding up of railway vehicles, and a large output design has been incorporated into the main motor that drives the axle. Since the main motor for railway vehicles is configured in a narrow space in the carriage, it is limited to enlarge the main motor itself, and it is necessary to increase the output while maintaining the same size as the conventional motor.

  By the way, since a railway vehicle such as an electric locomotive requires high output, it is fitted to the rotor shaft end of the main motor without interposing a coupling (coupling) between the main motor and the axle. A structure is adopted in which the rotational power of the main motor is directly transmitted to the axle via a drive device comprising a pinion (small gear) and a gear (large gear) fitted to the axle so as to mesh with the pinion (for example, a patent) Reference 1).

  FIG. 8 is a longitudinal sectional view showing the relationship between a main motor for a locomotive (rotary electric machine for a railway vehicle) and a driving device according to the prior art disclosed in Patent Document 1 and the like. 9 is a cross-sectional view of FIG. 8, and FIG. 10 is an enlarged cross-sectional view of the bearing device on the drive device side.

First, in FIG. 8, sandwiched by space portion to the pair of wheels 1 _-1 and 1 _-2 rotatably supported in carriage, not shown, for example, the main motor 2 comprised of squirrel-cage induction motor rotor A shaft (also called a drive shaft) 3 is installed so as to be parallel to the axle 4.

  Reference numeral 5 denotes a stator of the main motor 2, and a stator core 5a made of steel plates stacked in an annular shape and a stator winding 5b housed in a winding slot provided on the inner peripheral surface of the stator core 5a. It is composed of Reference numeral 6 denotes a rotor arranged concentrically with the stator core, which is composed of a rotor core 6a and a secondary conductor (cage-type conductor) 6b, and the rotor shaft 3 is arranged at the center of the rotor core 6a. Is inserted. Reference numeral 7 denotes a stator frame that supports the stator core 5a, and is fixed to a carriage or the like.

  A bearing bracket 8 is attached to an opening end of the stator frame 7 on the drive device (described later) side, and a bearing housing portion 8a is integrally formed at the center. A cylindrical roller bearing 9 is fitted and held in the bearing housing portion 8a so as to withstand a large radial load.

  Reference numeral 10 denotes an independent bearing housing attached to the end of the stator frame 7 on the side opposite to the driving device. The bearing housing 10 includes a cylindrical roller with a flange so that it can withstand a thrust load acting on the side opposite the driving device. The bearings 11 are respectively fitted. The cylindrical roller bearing 9 and the flanged cylindrical roller bearing 11 are configured to rotatably support the rotor shaft 3. Reference numerals 12 and 13 are respectively attached to the bearing housing portion 8a and the bearing housing 10 with bolts or the like, and press the outer rings of the cylindrical roller bearing 9 and the flanged cylindrical roller bearing 11 from the side surfaces to thereby press the bearing housing portion 8a and the bearing housing 10 respectively. It is an end cover for firmly fitting and holding.

  The portion consisting of the bearing housing 8a, the cylindrical roller bearing 9 and the end lid 12 is called a bearing device on the driving device side, and the portion consisting of the bearing housing 10, the flanged cylindrical roller bearing 11 and the end lid 13 is on the counter driving device side. It is called a bearing device.

14 is provided adjacent to the bearing device of the drive device side, a drive for transmitting the drive torque of the main motor 2 wheels 1 _-1, 1 _-2. The drive device 14 is fitted to the axle 4 and a cylindrical pinion 15 having a mounting hole fitted on the outer peripheral portion of the shaft end portion of the rotor shaft 3 protruding from the bearing bracket 8 and teeth on the outer peripheral surface. A gear 16 that is worn and has teeth that mesh with the pinion 15 on the outer peripheral surface, and a gear case 17 that encloses a lubricating oil 18 for lubricating the meshing surfaces of the pinion 15 and the gear 16.

As schematically shown in FIG. 9, the drive device 14 stores a lubricating oil 18 so that the lower portion of the gear 16 is immersed. The gear case 17 has a portion in contact with the axle 4 and the end cover 12 of the bearing device on the driving device side so that no oil leaks even if the lubricating oil 18 is stirred and scattered by the rotation of the gear 16. An oil seal 19 is provided (see FIGS. 8 and 10). 20 is a rail to put the wheels _{1 -1, 1 -2.}

  In the prior art, as shown in FIG. 10, as a lubricant for the cylindrical roller bearing 9 constituting the drive device side bearing device, grease oil 21 is filled in pocket portions formed on both sides of the cylindrical roller bearing 9 of the bearing housing 8a. The cylindrical roller bearing 9 is lubricated with the grease oil 21. In the figure, 22 and 23 are oil drainers. Note that the bearing device on the side opposite to the driving device is also configured to lubricate the flanged cylindrical roller bearing 11 with grease oil.

  By the way, the electric locomotive employs a structure in which the power of the pinion 15 is directly driven via the gear 16 without using a joint (coupling) as described above. Compared to the coupling space that is no longer necessary, the space for the main motor can be used, and as a result, the size of the main motor can be increased.

  Naturally, if the main motor 2 is enlarged, a large output torque can be obtained. Therefore, the pinion 15 and the gear 16 have a tooth width and a tooth thickness, and further the pinion 15 rotates from the tooth bottom of the pinion 15 so as to withstand this large output torque. Dimensions such as the wall thickness up to the inner circumference fitted to the slave shaft are determined by calculation. The dimensions of these parts tend to increase in proportion to the increase in the torque of the main motor 2. Similarly, on the rotor shaft 3 of the main motor 2 to which the pinion 15 is fitted, the torque reaction force of the gear 16 is received by the pinion 15 to generate a bending moment, and the magnitude of the bending moment is proportional to the torque reaction force.

  When the traction force of the electric locomotive is increased, it is necessary to increase the gear ratio as the output torque of the main motor 2 increases. The gear ratio can be increased by increasing the number of teeth of the gear 16 as much as possible, and conversely by decreasing the number of teeth of the pinion 15. However, the pinion 15 and the gear 16 need to increase the tooth thickness as much as possible in order to increase the tooth strength, and the module indicating the tooth size cannot be reduced.

When this module cannot be reduced, increasing the number of teeth of the gear 16 increases the diameter of the tip circle of the gear 16. Tip diameter of the gear 16, a wheel 1 _-1 mounted on the same axle as the gear _16, must be smaller than the diameter of 1 _-2. This is because the bottom surface of the gear case 17 covering the gear 16 will exceed the vehicle critical dimension unless the gear tip circle diameter is made smaller than the wheel diameter. For this reason, when the module which shows the size of a tooth cannot be made small, there is a limit in increasing the number of teeth of the gear 16 from the relation of the vehicle limit dimension, and the number of teeth cannot be increased beyond a certain level. .

On the other hand, in order to increase the gear ratio by reducing the number of teeth of the pinion 15, the dimension from the pinion tip diameter and the root circle diameter to the inner circumference where the pinion 15 is fitted to the rotor shaft 3 ( It is necessary to reduce the thickness), but if the thickness from the tooth bottom to the fitting hole (inner circumference) of the pinion 15 is reduced, the 15 strength of the pinion is insufficient, which is also limited. .
Further, when the torque of the main motor 2 is increased, the bending moment generated in the rotor shaft 3 is increased. Accordingly, in the main motor 2 having a large torque, it is necessary to make the rotor shaft 3 thicker.

  Increasing the thickness of the rotor shaft 3 also increases the inner diameter of the cylindrical roller bearing 9 on the pinion 15 side, which in turn increases the bearing diameter. As a result, the DmN value obtained by multiplying the average value of the outer diameter and inner diameter of the bearing indicating the peripheral speed of the cylindrical roller bearing 9 by the number of rotations is increased, and exceeds the peripheral speed limit suitable for grease oil lubrication. In this case, the so-called grease oil lubricated bearing in which the cylindrical roller bearing 9 is filled with the grease oil 21 as shown in FIG. 10 becomes impossible.

  As described above, the increase in torque of the locomotive main motor is limited because the pinion 15, the gear 16, the rotor shaft 3 of the main motor, and the cylindrical roller bearing 9 on the driving device are in a relationship in which the strength and the bearing DmN value are mutually contradictory. Has occurred.

Further, in a large torque main motor, the fitting force between the pinion 6 and the rotor shaft 3 also needs to be increased. In order to increase the fitting force, the diameter of the fitting hole is increased or the fitting length is increased. It is necessary to do. The increase in the diameter of the fitting hole is limited because the dimension of the inner periphery from the bottom of the pinion 15 decreases as described above. Since When the longer fitting length will increase the face width of the pinion 15, the main motor 2 on both sides of the wheel 1 _-1, since it is configured sandwiched 1 _-2, main motor 2 This is difficult unless the axial length is shortened. It is impossible to shorten the main motor because it is against the increase in torque of the main motor.

  In order to solve these problems and achieve a main motor with high output, the inventor has a tapered fitting at the end of the rotor shaft 3 located in the bearing device on the drive device 14 side as shown in FIG. A so-called fitting shaft-integrated pinion 15A in which a shaft 15a and a pinion 15 that are fitted into the tapered fitting hole 3a are formed in a hollow state by opening the fitting hole 3a has been considered.

  Even if the number of teeth of the shaft-integrated pinion 15A is reduced in order to increase the gear ratio, the fitting shaft-integrated pinion 15A has a solid shaft. Since there is no limit regarding the dimension from the root to the inner peripheral surface of the fitting hole, the gear ratio can be increased. Similarly, when the rotor shaft 3 is made thick due to the influence of bending moment, there is no particular problem because the pinion 15A is a solid shaft. Further, the fitting force can be increased by increasing the inner diameter of the inner ring of the cylindrical roller bearing 9. By increasing the depth dimension of the tapered fitting hole 3 a provided in the rotor shaft 3 of the main motor 2, the fitting force can be increased without affecting the length of the main motor 2.

As described above, when the fitting shaft-integrated pinion is adopted, the inner shaft inner diameter of the cylindrical roller bearing 9 is increased because the rotor shaft 3 of the fitting shaft-integrated pinion 15A is thickened, and as a result, the cylindrical roller bearing 9 is expanded. In this case, the DmN value of the bearing 9 is increased, and the conventional structure constituted by grease lubrication exceeds the DmN value of 60 × 10 ⁴ generally applied for grease lubrication. In this case, as a countermeasure, it is conceivable to adopt a lubricating oil circulation system in which the DmN value can be set higher.

  In the case of the lubricating oil circulation system shown in FIG. 11, the lubricating oil used for lubricating the pinion 15 and the gear 16 in the gear case 17 provided adjacent to the bearing device on the drive device 14 side is introduced into the bearing. Is possible.

  Specifically, in order to introduce the lubricating oil 18 that lubricates the teeth of the gear 16 and the pinion 15 in the gear case 17 into the adjacent bearing device, the flange 24 protrudes toward the gear 16 on the upper portion of the end cover 12. The lubricating oil 18 stirred by the gear 16 inside the gear case 17 is collected by the flange 24 by providing the end cover 12 with an oil supply hole 25 that communicates between the flange 24 and the inside of the bearing device. What is necessary is just to make it the structure which flows into the inside of the cylindrical roller bearing 9 from the oil supply hole 25 provided in the lid | cover 12, and returns the lubricating oil 18 which finished lubrication to the gear case 17 from the oil drain hole 26 provided in the lower part of the end cover 12.

JP 2007-74856 A

  By the way, a main motor for a railway vehicle needs to be subjected to a performance test as a single main motor before assembling with a bogie or gear of an electric locomotive. That is, it is necessary to verify the performance of the main motor 2 with the gear 16 and the gear cover 17 of the drive unit omitted, and to confirm the quality of the main motor 2, so that the lubricating oil 18 in the gear case 17 is required during the unit test. This causes a problem that it cannot be guided to the ridge 24.

  In order to supply lubricating oil to the cylindrical roller bearing 9 by the main motor 2 alone, it is conceivable that the lubricating oil is forcibly poured into the flange 24. It flows out from the oil drain hole 26 to the outside. This main motor rotation test is performed by the main motor manufacturer when the main motor is manufactured, but even when the end user reassembles the electric locomotive after overhaul, the main motor itself is tested for rotation. It is necessary to confirm the performance, and the lubrication method of the bearing with the main motor alone becomes a problem.

  Therefore, in order to solve the above-described problems, the present invention is configured to fit the pinion shaft of the shaft-integrated pinion into a fitting hole formed in the shaft end on the drive device side of the locomotive main motor, and to provide a lubricating oil for the drive device. In a rotating electrical machine for a railway vehicle that is configured to circulate in common with the bearing device. An object of the present invention is to provide a bearing device.

In order to achieve the above object, the invention according to claim 1 is arranged such that the axle of the railway vehicle and the rotor shaft of the rotating electrical machine are arranged in parallel and fitted to a bearing housing formed on the bearing bracket of the rotating electrical machine. The driving torque of the rotating electrical machine is transmitted to the wheels via a driving device comprising a pinion attached to the end of the rotor shaft passing through the held bearing and a gear attached to the axle so as to mesh with the pinion. The end cover of the bearing device attached to the bearing housing is configured as a part of a gear case that accommodates the driving device, and a part of the lubricating oil that lubricates the driving device in the gear case is formed. In a bearing device for a rotating electrical machine for a railway vehicle that is shared as lubricating oil for the bearing device, a hole in the axial direction is formed at the end of the rotor shaft, and the hole is integrally formed with the pinion. A fitting shaft is fitted and fixed, and a flange that collects the lubricating oil agitated by the driving device with respect to an end cover of the bearing device that is located in the gear case, and the lubricating oil collected by the cage is a bearing device. An oil supply hole for supplying an internal bearing, an oil discharge hole for discharging the lubricating oil lubricated in the bearing, and a lubricating oil reservoir for storing the lubricating oil discharged from the oil draining hole are provided. It is characterized in that the oil level of the lubricating oil to be stored is above the rolling surface between the rolling element of the bearing and the inner diameter of the outer ring.

  According to the present invention, the lubricating oil reservoir is provided in the lower portion of the end cover of the bearing device on the drive device side, so that the lubricating oil can be applied to the eaves formed on the upper portion of the end cover during the rotation test of the main motor alone. As a result, lubricating oil is supplied into the bearing from the oil supply hole of the end lid that communicates with the inside of the bearing from the flange, and the lubricating oil that lubricated the bearing is stored in the lubricating oil reservoir at the bottom of the end lid, so there is no gear case or gear Even in the state, the lubricating oil can be supplied to the bearing on the drive device side.

Sectional drawing of the drive device side bearing apparatus of the rotary electric machine for railway vehicles by Embodiment 1 of this invention. FIG. 2 is a cross-sectional view of the rotating electrical machine for a railway vehicle and the drive device according to Embodiment 1 shown in FIG. 1. Sectional drawing of the drive device side bearing apparatus at the time of carrying out the unit test of the rotary electric machine for rail vehicles by Embodiment 1 of this invention. Sectional drawing of the drive device side bearing apparatus of the rotary electric machine for railway vehicles by Embodiment 2 of this invention. Sectional drawing of the drive device side bearing apparatus of the rotary electric machine for railway vehicles by Embodiment 3 of this invention. Sectional drawing of the drive device side bearing apparatus of the rotary electric machine for railway vehicles by Embodiment 4 of this invention. Sectional drawing of the drive device side bearing apparatus of the rotary electric machine for railway vehicles by Embodiment 5 of this invention. The longitudinal cross-sectional view which shows the relationship between the rotary electric machine for rail vehicles by a prior art, and a drive device. FIG. 9 is a cross-sectional view of a rotating electrical machine for a railway vehicle and a driving device according to the prior art shown in FIG. 8. Sectional drawing of the drive device side bearing apparatus by a prior art. Sectional drawing of the drive device side bearing apparatus by the improvement plan of a prior art.

Hereinafter, embodiments of the present invention will be described.
In addition, the overlapping description shall be suitably abbreviate | omitted by attaching | subjecting the same code | symbol to the same components and the same part throughout each figure.

(Embodiment 1)
1 is an enlarged view showing a drive device side bearing device of a rotating electrical machine for a railway vehicle according to Embodiment 1 of the present invention, FIG. 2 is a cross-sectional view of the rotating electrical machine and the driving device of FIG. 1, and FIG. It is sectional drawing of the drive device side bearing apparatus at the time of carrying out a unit test.

  As shown in FIGS. 1 and 2, the first embodiment is fixed to the bearing housing portion 8 a of the bearing bracket 8 attached to the opening end portion of the stator frame (not shown) on the driving device side as shown in FIG. 11. A cylindrical roller bearing 9 is configured to rotatably support one end of the rotor shaft 3 of the main motor 2. A tapered fitting hole 3a having a depth substantially the same as the width of the bearing housing portion 8a is formed along the rotor shaft direction at an end portion of the rotor shaft 3 protruding or exposed from the bearing bracket 8. In addition, the fitting shaft 15a of the fitting shaft-integrated pinion 15A in which the teeth 15 and the fitting shaft 15a are integrated into the fitting hole 3a is fitted and fixed.

  The end lid 12 attached to the side surface of the bearing housing portion 8a with a fixing member such as a bolt constitutes a part of the side wall of the gear case 17. In the gear case 17, a flange 24 that collects the lubricating oil 18 that has been agitated and scattered by the rotation of the gear 16 is provided at the upper position of the end cover 12 (above the pinion teeth 15). An oil supply hole 25 that communicates between the flange 24 and the cylindrical roller bearing 9 inside the bearing housing portion 8a is provided. Further, an oil drain hole 26 for discharging the lubricating oil 18 that lubricates the cylindrical roller bearing 9 is provided at the lower portion of the end lid 12, and lubrication for maintaining the oil level of the lubricating oil 18 discharged from the oil drain hole 26 at a constant level. An oil reservoir 27 is provided.

  Here, the oil surface 18L when the lubricating oil 18 is stored in the lubricating oil reservoir 27 is such that the rolling surfaces of the rolling elements 9a of the cylindrical roller bearing 9 and the inner diameter of the outer ring 9b are always immersed in the lubricating oil. It is designed to be always higher than the running surface.

  In the drive device side bearing device of the rotating electrical machine for a railway vehicle configured as described above, when the main motor 2 is subjected to a rotation test alone, the gear 16 and the gear case 17 are removed from the state shown in FIG. Then, the lubricating oil 18 is supplied to the flange 24 provided on the upper portion of the end lid 12.

  Then, the lubricating oil 18 enters the bearing housing 8 a through the oil supply hole 25, lubricates the cylindrical roller bearing 9, is discharged from the oil drain hole 26 provided in the lower part of the rear end cover 12, and is formed in the lower part of the end cover 12. The oil is stored in the lubricating oil reservoir 27.

  As a result, the lubricating oil 18 always supplies the rolling surface of the cylindrical roller bearing 9, so that even in the rotation test of the main motor 2 alone, it is not necessary to supply the lubricating oil from the gear case 17, and the cylindrical roller bearing 9. It becomes possible to lubricate.

  If the main motor 2 is rotated in a normal operation state where the gear 16 and the gear case 17 are attached to the main motor 2, the lubricating oil 18 scattered by the gear 16 is continuously collected in the rod 24. 18 is once stored in the lubricating oil reservoir 27 and then overflows and is returned to the gear case 17.

  Further, in the first embodiment, since the end cover 12 also serves as a part of the side wall of the gear case 17, the dimensions from the bearing bracket 8 to the drive device 14 can be shortened, and the rotating electrical machine and the drive device are included. There is an effect that the entire configuration can be reduced in size.

(Embodiment 2)
FIG. 4 is a diagram showing a drive device side bearing device of a rotating electrical machine for a railway vehicle according to Embodiment 2 of the present invention.
In FIG. 4, in the second embodiment, a flange 24 and an oil supply hole 25 are formed in the upper part of the end cover 12, and a lubricating oil reservoir 27 is formed in the lower part of the end cover 12, as will be described with reference to FIGS. However, in the second embodiment, the end cover 12 is made of cast material, and the lubricating oil reservoir 27 is cast integrally with the end cover 12.

The lubricating oil reservoir 27 is thick because it is made of casting, but the upper surface of the lubricating oil reservoir 27 is located above the rolling surface of the rolling element 9a of the cylindrical roller bearing 9 and the inner diameter of the bearing outer ring 19b. There is no change in the configuration.
In the second embodiment, in addition to the operational effects of the first embodiment, when the end lid 12 is cast, the lubricating oil reservoir 27 is integrally cast, so that the number of manufacturing steps can be reduced.

(Embodiment 3)
FIG. 5 is a diagram showing a drive device side bearing device for a rotating electrical machine for a railway vehicle according to Embodiment 3 of the present invention.
In FIG. 5, the third embodiment is different from the first embodiment or the second embodiment in that the lubricating oil reservoir 29 is configured inside the end lid 12 without protruding outside the end lid 12. Is a point. Reference numeral 28 denotes an air escape hole for removing air from the lubricating oil reservoir 29 so that the lubricating oil 18 becomes a predetermined oil level 18L. In cases other than the unit test of the main motor 2, the lubricating oil 18 overflows from here. The gear case 17 is then reduced.

  In the case of the third embodiment, the amount of lubricating oil stored in the lubricating oil reservoir 29 is reduced, but the oil surface 18L of the lubricating oil reservoir 29 rolls between the rolling elements 9a of the cylindrical roller bearing 9 and the inner diameter of the bearing outer ring 9b. By configuring so as to be always above the surface, it is possible to achieve the same operational effects as in the first and second embodiments.

(Embodiment 4)
FIG. 6 is a view showing a drive device side bearing device of a rotating electrical machine for a railway vehicle according to Embodiment 4 of the present invention.
In FIG. 6, the fourth embodiment is different from the third embodiment in that the lubricating oil reservoir 29 is formed inside the end lid 12 in the third embodiment. However, in the fourth embodiment, the lubricating oil reservoir 30 is provided. It is formed inside the bearing housing portion 8a.

Also in the case of the fourth embodiment, the oil surface 18L of the lubricating oil reservoir 30 inside the bearing housing portion 8a is more than the rolling surface of the rolling element 9a of the cylindrical roller bearing 9 and the inner diameter of the bearing outer ring 9b as in the third embodiment. Although it is configured so as to be on the upper side, a communication hole through which the lubricating oil is directly reduced from the lubricating oil reservoir 29 of the bearing housing portion 8a is not provided in the gear case 17, and the end cover 12 is connected to the inside of the cylindrical roller bearing 9. The communication hole 31 that communicates with the gear case 17 is configured to be above the rolling surface between the rolling element 9a of the cylindrical roller bearing 9 and the inner diameter of the bearing outer ring 9b.
Also in the fourth embodiment, the same operational effects as those of the already described embodiments can be obtained.

(Embodiment 5)
FIG. 7 is a view showing a drive device side bearing device of a rotating electrical machine for a railway vehicle according to Embodiment 5 of the present invention.
In FIG. 7, the fifth embodiment is a combination of the third embodiment of FIG. 5 and the fourth embodiment of FIG. That is, in the fifth embodiment, the lubricating oil reservoir 27 is configured in both the inside of the end lid 12 and the inside of the bearing housing portion 8a. Even in the case of the fifth embodiment, there is no change in that the oil surfaces of the lubricating oil reservoirs 27 and 30 are configured to be above the rolling surfaces of the rolling elements 9a of the cylindrical roller bearing 9 and the inner diameter of the bearing outer ring 9b.

According to the fifth embodiment, it is possible to increase the amount of the lubricating oil 18 that can be stored approximately twice as much as the case where the lubricating oil reservoir is formed only in the end lid 12 or the bearing housing portion 8a.
As a result, there is an advantage that it is not necessary to replenish the lubricating oil even if the rotation test time of the main motor is long.

  DESCRIPTION OF SYMBOLS 3 ... Shaft, 3a ... Tapered fitting hole, 8 ... Bearing bracket, 8a ... Bearing housing part, 9 ... Cylindrical roller bearing, 9a ... Rolling element, 9b ... Bearing outer ring, 12 ... End cover of bearing device, 15 ... Pinion (Small gear), 15a ... fitting shaft, 15A ... fitting shaft integrated pinion, 16 ... gear (large gear), 17 ... gear case, 18 ... lubricating oil, 24 ... ２４, 25 ... oil supply hole, 26 ... drain oil Hole, 28 ... Air escape hole, 27, 29, 30 ... Lubricating oil reservoir, 31 ... Communication hole.

Claims (5)

A pinion attached to the end of the rotor shaft, which is arranged in parallel with the axle of the railway vehicle and the rotor shaft of the rotating electrical machine and passes through a bearing fitted and held in a bearing housing formed on the bearing bracket of the rotating electrical machine, and An end cover of the bearing device attached to the bearing housing , wherein the driving torque of the rotating electrical machine is transmitted to the wheel via a driving device comprising a gear attached to the axle so as to mesh with the pinion. As a part of a gear case that houses the driving device, and a part of the lubricating oil that lubricates the driving device in the gear case is shared as the lubricating oil for the bearing device. In the bearing device of
A hole in the axial direction is formed at the end of the rotor shaft, and an attachment shaft formed integrally with the pinion is fitted and fixed in this hole,
A hook that collects the lubricating oil agitated by the driving device with respect to the end lid of the bearing device located in the gear case, and an oil supply hole that supplies the lubricating oil collected by the hook to a bearing inside the bearing device And an oil drain hole for discharging the lubricating oil lubricated in the bearing, and a lubricating oil reservoir for storing the lubricating oil discharged from the drain oil hole, respectively, and the oil level of the lubricating oil stored in the lubricating oil reservoir A bearing device for a rotating electrical machine for a railway vehicle, characterized in that is positioned above the rolling surface between the rolling elements of the bearing and the inner diameter of the outer ring.   The bearing device for a rotating electrical machine for a railway vehicle according to claim 1, wherein the end cover of the bearing device and the lubricating oil reservoir are integrally formed by casting.   The bearing device for a rotating electrical machine for a railway vehicle according to claim 1, wherein the lubricating oil reservoir is formed inside an end cover of the bearing device. The bearing device for a rotating electrical machine for a railway vehicle according to claim 1, wherein the lubricating oil reservoir is formed inside the bearing housing instead of being provided on an end cover of the bearing device.   2. The bearing device for a rotating electrical machine for a railway vehicle according to claim 1, wherein the lubricating oil reservoir is formed inside an end lid and a bearing housing of the bearing device.

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