JP2002195273A - Bearing unit - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a bearing unit capable of further improving durability and reliability. SOLUTION: A seizure resistant property of a bearing supporting a driving axle in a driving gear of a rolling stock can be considerably improved by using tapered roller bearings 113 and 114 whether it is starting time or running time. There are not any problems such as reduction of load rating and increase of a bearing size because the tapered roller bearings are the same as normal tapered roller bearings 13 and 14 except the position of rib portions 113d and 114d. Further, as adjustment of bearing clearance and assembling works to equipment can be done in a similar method as well as those of a conventional tapered roller bearing, a change of peripheral structure surrounding the bearings in the driving gear, introduction of new working facilities, and work training and the like can be minimized.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a bearing device suitable for being incorporated in an increase / decrease device such as a drive device for a railway vehicle or a differential gear device for an automobile.

[0002]

2. Description of the Related Art In order to increase / decrease the output of a motor, an engine, or the like, an increasing / decreasing device which combines gears is known. FIG. 4 is a schematic plan view showing a drive mechanism of a railway vehicle, and FIG. 5 is a schematic side view thereof. In the figure, a driving motor 1 is connected to a small gear 3 via a coupling 2. The large gear 4 meshing with the small gear 3
The axle 5 is connected to both ends of the axle 5 by rails 6.
A wheel 7 that rolls on is mounted. The small gear 3 and the large gear 4 are helical gears.

FIG. 6 is an axial sectional view of a driving device 10 including a small gear 3 and a large gear 4. In FIG. 6, a drive shaft 12 connected to a drive motor 1 has a housing 11
Are supported by tapered roller bearings 13 and 14. The drive shaft 12 has the small gear 3 mounted between the tapered roller bearings 13 and 14. The large gear 4 meshing with the small gear 3 is attached to the axle 5, and the axle 5 is rotatably supported with respect to the housing 11 by tapered roller bearings 15 and 16 arranged so as to sandwich the large gear. Have been.

The rotation output of the drive motor 1 is transmitted to the drive shaft 12 via the coupling 2, and further reduced while being transmitted from the small gear 3 to the large gear 4, transmitted to the axle 5, and 7 is rotated.

Here, the tapered roller bearings 13 and 14 for supporting the drive shaft 12 are helical gears composed of the small gear 3 and the large gear 4, so that the gears at the time of driving caused by their tooth shapes are formed. In order to support a reaction force, it is required to have a certain load capacity with respect to axial and radial loads.
Due to such characteristics, generally, two tapered roller bearings are often used in frontal combination as shown in FIG.

FIG. 7A is a view showing the tapered roller bearing 14 taken out, and FIG. 7B is a view of a part of the tapered roller bearing 14 shown in FIG. It is. In FIG. 7, the tapered roller bearing 14 includes an outer ring 14a, an inner ring 14b, and a tapered roller 14c.
A collar 14d is formed at the left end of the inner race 14b in FIG.

[0007]

By the way, the driving device 1
The axial load Fa applied to the tapered roller bearing 14 at the time of the operation 0 is mainly supported by the flange portion 14d of the inner ring 14b and the opposed end face 14f of the tapered roller 14c. In these contact areas B (FIG. 7 (b)), since rolling contact accompanied by a large slip occurs, thorough control of the amount of lubricating oil supplied to the tapered roller bearings 14 so that seizure does not occur in this area. There is a need to. However, in the drive device, lubrication of each tapered roller bearing and gears is performed by the housing 11.
Oil G (FIG. 4) stored in the lower part of the gear is lifted up by the large gear 4.
There is a problem that the lubrication conditions are deteriorated due to the following reasons. (Cause of deterioration in lubrication conditions) Lubricant oil viscosity is high and it is difficult to flow (the large gear cannot sufficiently lift up oil). When the vehicle is stopped for a long time, the lubricating oil in the bearings flows out, and at the time of starting, the bearings 13 and 14 start rotating without sufficient lubricating oil. Immediately after the start, the temperature of the drive shaft 12 side rises more rapidly than the housing 11 side. Therefore, if the increase in the size of the drive shaft 12 due to thermal expansion exceeds the increase in the size of the housing 11 side,
The bearing clearance set at room temperature may be blocked, resulting in an excessive bearing load.

In addition, during high-speed running, the PV value in the contact area between the flange portion and the end face becomes large. Therefore, it is required that the anti-seizure property is excellent even during normal running other than low-temperature starting. In order to solve these problems, the following methods have conventionally been adopted. (Solution method) The bearing supporting the drive shaft is a combination of a four-point contact ball bearing and a cylindrical roller bearing (Japanese Utility Model Laid-Open No. 64-3835l). The drive shaft is supported by a cylindrical roller bearing and a cylindrical roller bearing with double flanges (Japanese Patent Application Laid-Open No. 2000-18342, Japanese Patent Application Laid-Open
18242). The bearing supporting the drive shaft is a tapered roller bearing in a back-to-back combination, and the housing side is made of a material having a larger linear expansion coefficient than that of the drive shaft side (Japanese Utility Model Laid-Open No. 2-19965). An elastic body is provided on the bearing outer ring supporting the drive shaft and an axial fitting surface of the housing so that an excessive load is not applied to the bearing even when the bearing generates heat and the clearance is closed (Japanese Patent Application Laid-Open No. 10-252763). Gazette).

Here, according to the solution according to the prior art, it is not necessary to adjust a bearing axial gap required for supporting a tapered roller bearing, thereby improving maintainability. Since lubricating oil accumulates, certain effects are recognized in preventing seizure during startup.
However, in the solution method, since a ball bearing is used, in order to obtain the same load capacity as a tapered roller bearing, there are problems such as an increase in bearing size, a shortened life, and an increase in cost. On the other hand, the solution method has problems such as an improvement in the axial load capability of the flange portion of the cylindrical roller bearing, a high-speed rotation (improvement in seizure resistance under high PV conditions), and a cost problem.

Furthermore, the conventional solutions have various problems that must be solved before practical use, such as complicated material selection and the structure around the bearings, and the degree of effectiveness is unknown. . There is also a problem that using a special material or structure leads to an increase in cost.

An object of the present invention is to provide a bearing device capable of further improving durability and reliability in view of the problems of the related art.

[0012]

SUMMARY OF THE INVENTION A bearing device according to the present invention includes an outer ring integrally formed with a flange portion extending at least in one end in the axial direction toward a radially inward direction, an inner ring, and the outer ring and the inner ring. And a plurality of rollers that can roll freely between the rollers and are used for a drive device of a vehicle.

[0013]

[Action] Generally, in a rolling bearing having a contact angle (tapered roller bearing, angular contact ball bearing), a function of drawing oil into the inside of the bearing by a centrifugal pump action accompanying the rotation of the bearing (hereinafter referred to as a pump action) works, and the diameter of the bearing increases from the smaller diameter side. A lubricating oil flow is generated toward the side. It is known from literatures and the like that the oil flow inside a bearing affects the bearing performance (life, seizure, torque, etc.) (for example, RL Leibensper).
ger; Trans. ASME, J.A. of Lub-T
ech, April, 1972, Toda et al .: Tribologist, vol. 42, No. 4, p. 308-31
1, 1997, etc.).

The present inventors observed the oil flow inside the bearing under the conditions equivalent to the actual machine (rotational speed, lubricating oil viscosity) using a tapered roller bearing whose outer ring was made of acrylic. A high-speed video camera (maximum 2000 frames / second) was used for shooting.

FIG. 8 is an axial sectional view of a model of a tapered roller bearing with an inner ring flange including a retainer used in the experiment of the present inventors. With reference to FIG. 8, what has been found by the experiments of the present inventors will be described. The lubricating oil is drawn into the bearing from between the inner circumference of the cage and the outer circumference of the inner ring on the small diameter side of the bearing ((I) in the figure). Low speed range (vehicle speed conversion = (a) 60 km / h or less; if the vehicle is a Shinkansen, (b) 30 km / h or less; if the vehicle is a conventional line, (c) 20 km / h or less; if the vehicle is a car) Most of the lubricating oil drawn into the bearings moves to the space between the outer circumference of the cage and the outer circumference of the outer ring from the gap between the columns of the cage under the influence of centrifugal force, except for ((II) in the figure), it is discharged from the bearing large diameter side through this space ((III) in the figure). Since the lubricating oil moves to the outer ring side by centrifugal force, there is almost no lubricating oil flow to the brim side except in the low speed range ((IV) in the figure). Oil attached to the roller surface is supplied only to the flange by the rotation of the rollers, and the amount of oil supplied is extremely small.

As described above, in most speed ranges except the low speed range, the lubricating oil flow is guided to the outer ring side by the influence of centrifugal force. Therefore, in the tapered roller bearing having the outer ring provided with the flange portion as in the present invention, Compared with a normal tapered roller bearing, a large amount of lubricating oil can be secured to reach the flange portion, so that seizure resistance is significantly improved. In particular, there is a remarkable effect of improving seizure resistance under high PV conditions (during high-speed running) where seizure resistance during running is a problem.

Further, in a tapered roller bearing provided with a flange portion on the outer ring, the flange portion on the inner ring side can be reduced or omitted structurally, so that the opening area on the small diameter side of the bearing is increased and a large amount of oil is supplied into the bearing. It is possible to introduce. The small-diameter-side opening area of the bearing is a clearance area between the small-diameter-side cage inner diameter and the inner-ring small-diameter side outer diameter. The larger this portion is, the easier it is to introduce lubricating oil into the bearing. Also, if the small-diameter side opening area is the same as a tapered roller bearing provided with a flange portion on a normal inner ring, the cage small-diameter side flange can be enlarged by the amount of no collar portion on the inner ring, This is also advantageous in terms of the strength of the retainer. The tapered roller bearing in which the outer ring is provided with the flange portion has an advantage that the degree of freedom in designing the small-diameter side internal specifications is improved.

A PV value is generally used as a parameter of seizure resistance. Here, the PV value of the flange portion and the roller end will be considered. If the contact height is the same for both the configuration with the collar on the outer ring and the configuration with the collar on the inner ring, the configuration with the collar on the outer ring is better than the configuration with the collar on the inner ring. And the relative sliding speed (V) with respect to the flange portion is reduced. Although depending on the specifications of the bearing, in most tapered roller bearings, the sliding speed of the outer ring flange is 30 to 35% lower than the sliding speed of the inner ring flange. There is almost no difference in the surface pressure (P). From the above, the PV value under the same load / rotational speed condition is smaller in the configuration in which the collar is provided on the outer ring, and the tapered roller bearing in which the collar is provided in the outer ring also has a seizure resistance from the viewpoint of PV value. Effective for improvement.

In a normal tapered roller bearing, since the inner diameter of the outer ring is merely a tapered surface, all the oil in the bearing flows out of the bearing when the bearing is stopped, but the tapered roller bearing having the outer ring provided with a flange portion. Then, it is stored below the outer ring. In other words, since the collar functions as a dam that blocks the lubricating oil, the lubricating oil is stored in this part when the bearing is stopped, and the lubricating oil is kept in the bearing even when starting after a long stop Begin to. Therefore, the lubricating oil is ensured in the bearing even under severe conditions such as a low temperature start in winter, so that the tapered roller bearing having the outer ring with the flange portion is highly effective in preventing seizure. Further, even if the supply of the lubricating oil is stopped for some reason during the rotation of the bearing, the flange of the outer ring functions as a dam, and the lubricating oil can be temporarily held in the bearing. From this point of view, it is also effective in preventing seizure.

Since there is no difference in configuration from a normal tapered roller bearing except for the position of the flange portion, problems that may occur in the above-described other type of bearing system, such as load capacity and bearing size, are avoided.

Since the bearing for the drive device only needs to be able to support an axial load in one direction, by providing the outer ring with a collar, the inner ring can be formed into a simple conical shape without the need for a collar. By forming the inner race into a simple conical shape without the flange, the flange of the outer race can be formed integrally with the outer race. In addition, the cage is integrally crimped with the outer ring and rollers, and the inner ring can be separated as a simple conical shape without a flange. ), It is possible to incorporate the bearing into the drive device in almost the same manner. Thereby, the design change of the bearing peripheral structure of the drive device can be minimized. Therefore, the bearing device of the present invention can be easily used as a substitute for a normal tapered roller bearing.

In summary, according to the present invention, by using a tapered roller bearing having a flange portion on an outer ring for a bearing device for a driving device such as a railway vehicle driving device or a differential device, the present invention is applied to a running bearing. When lubrication is temporarily stopped or when the drive is started, the collar of the outer ring functions as an oil reservoir, and during high-speed traveling, the centrifugal force can secure a sufficient amount of oil to the collar. In addition, the seizure resistance of the bearing can be improved irrespective of starting or running. In addition, since only the position of the flange portion is different, the load capacity and size are not different from those of a tapered roller bearing having a flange portion on a normal inner ring, and the handleability is excellent. Further, by caulking the cage integrally with the outer ring and the rollers, it is possible to incorporate the bearing into the drive device in almost the same manner as a normal tapered roller bearing (integrated with the inner ring, the rollers and the cage). The design change of the bearing peripheral structure of the drive device can be minimized.

[0023]

Embodiments of the present invention will be described below in detail with reference to the drawings. FIG. 1 is an axial cross-sectional view of a railway vehicle drive device 100 including the first embodiment. In FIG. 1, a drive shaft 12 connected to a drive motor (not shown) is supported by a housing 11 by tapered roller bearings 113 and 114. The drive shaft 12 has the small gear 3 mounted between the tapered roller bearings 113 and 114. Large gear 4 meshing with small gear 3
Are mounted on the axle 5 by tapered roller bearings 15 and 16 which are arranged so as to sandwich the large gear.
The axle 5 is rotatably supported by the housing 11.

The rotational output of a drive motor (not shown) is transmitted to the drive shaft 12, and further reduced while being transmitted from the small gear 3 to the large gear 4, transmitted to the axle 5, and rotates the wheels 7. It has become.

The tapered roller bearings 113, 114 constituting the bearing device of the present invention have outer rings 113a, 114a, inner rings 113b, 114b, and a plurality of tapered rollers 113c, 114c arranged between the two wheels. Outer ring 113
a and 114a have an end on the side of the small gear 3 (an end on a large diameter side).
And flange portions 113d and 114d extending inward in the radial direction.
Are integrally formed. The inner rings 113b, 114b
Does not have a brim portion.

Prior art conventional tapered roller bearings 13,1
In FIG. 4 (FIG. 6), since the inner diameter of the outer ring is merely a tapered surface, all the lubricating oil in the bearings 13 and 14 is discharged to the outside while the bearing is stopped. On the other hand, in the tapered roller bearing according to the present embodiment having the outer ring with a flange, the flanges 113d and 114d below the outer rings 113a and 114a.
However, since it functions as a dam for blocking the lubricating oil, the oil accumulates in this portion when the bearing is stopped, and the engine can be started with the oil secured in the bearing even after a long stop. Accordingly, sufficient lubricating oil is ensured even under severe conditions such as a low temperature start in winter, which is extremely effective in preventing seizure. Further, even when the supply of the lubricating oil is stopped for some reason during the operation of the bearing, the flanges 113 of the outer races 113a, 114a can be used.
d and 114d function as dams, and the bearing 11
Since the lubricating oil can be held in 3,114, there is an effect of preventing seizure.

The flow of the lubricating oil in the bearing is guided to the outer ring side under the influence of centrifugal force in almost all speed ranges. Therefore,
In the tapered roller bearings 113 and 114 of the present embodiment, compared to the tapered roller bearings 13 and 14 (FIG. 6) of the related art,
Since a large amount of oil can be secured to the flange portions 113d and 114d, seizure resistance is significantly improved. In particular, there is a remarkable effect of improving seizure resistance under high PV conditions (during high-speed running) where seizure resistance during running is a problem.

As described above, by using the tapered roller bearings 113 and 114 of the present embodiment, the seizure resistance of the bearing for supporting the drive shaft in the railway vehicle drive device is remarkably improved regardless of whether the vehicle is started or running. Can be improved. Since it is the same as the normal tapered roller bearings 13 and 14 (FIG. 6) except that the positions of the flange portions 113d and 114d are different, there is no problem such as a decrease in load capacity or an increase in bearing size due to the change of the bearing. . In addition, the adjustment of the bearing clearance and the work of assembling into the device can be performed by the same method as that of the conventional tapered roller bearing. Can be minimized. In the present embodiment, the present invention is applied only to the bearings 113 and 114 for supporting the drive shaft 12, but the present invention may be applied to the bearings 15 and 16 for supporting the axle 5.

FIG. 2 shows the results of comparison of the sliding speed (V) at the contact portion between the flange and the end face of the configuration in which the inner ring is provided with the collar portion and the configuration in which the outer ring is provided with the collar portion.
In this comparison, the inner diameter is 70 mm and the outer diameter is 150 mm
The contact height between the tapered roller bearing and the roller end face of the imported rib was calculated assuming that the height was the same as that of the inner ring side. As is clear from this drawing, the sliding speed (V) is about 3 times less in the configuration in which the outer ring is provided with the collar portion than in the configuration in which the inner ring is provided with the collar portion.
0% lower. Regardless of the size of the bearing, it is generally 30 to
The slip speed is reduced by about 35%.

By the way, in a tapered roller bearing in which a flange portion is provided on an outer ring, if the geometrical shape of a flange portion and an end face is the same as that of a tapered roller bearing in which a flange portion is provided on an inner ring, the contact surface pressure (P ) Is almost equal to the Hertzian elastic contact theory. Therefore, the PV value under the same operating conditions (the same load, the same rotation speed) is reduced by an amount corresponding to the decrease in the V (slip speed). Is effective in improving seizure resistance.

FIG. 3 is a sectional view of an automobile differential gear device (hereinafter referred to as a differential device) which is another example of the drive device. The differential device is a gear device that distributes and transmits the rotation of the engine transmitted via the transmission to the left and right tires, and also has a differential function.

More specifically, in the differential device 200 shown in FIG. 3, the differential drive shaft 212 rotatably supported by the tapered roller bearings 213 and 214 with respect to the differential case 201 has a ring gear at the left end in FIG. A pinion gear 203 that meshes with 204 is attached, and a flange 215 is attached to the right end in FIG. An inner ring spacer 216 is disposed between the tapered roller bearings 213 and 214.

Tapered roller bearing 21 with back (DB) combination
3 and 214 are outer rings 213a and 214a and an inner ring 213.
b, 214b and a plurality of tapered rollers 213c, 214c arranged between the two wheels.
4a, at the ends on the side separated from each other (ends on the large diameter side),
The flange portions 213d and 214d extending inward in the radial direction are integrally formed. Note that the inner rings 213b and 214b are not formed with a brim portion.

These tapered roller bearings 213, 214
In order to secure rigidity for improving the meshing accuracy of the pinion gear 203 and the ring gear 204 and to prevent sound and vibration,
Used in fixed position preload condition. Tapered roller bearing 213,
The lubrication of 214 is performed by scraping up the lubricating oil G stored in the differential case 201 with the rotating ring gear 204. The lubricating oil G scooped up by the ring gear 204 flows as shown by arrows (I) and (II) in the figure and is supplied to the tapered roller bearings 213 and 214. The lubricating oil G that has passed through the rear bearing 213 is
4, lubricating oil G penetrating through front bearing 214
Returns to the ring gear 204 side through a not-shown return path.

When a lateral acceleration acts, for example, when the vehicle is turning, the lubricating oil in the differential case 201 is biased to its side surface, so that the amount of lubricating oil that is scraped up by the ring gear 204 decreases, and the lubricating oil is applied to the tapered roller bearings 213 and 214. Refueling may decrease temporarily. At the time of rapid acceleration or low-temperature starting, the preload may be excessive due to uneven thermal expansion of each part due to a sudden increase in bearing temperature. If such a temporary decrease in the oil amount or excessive preload occurs, there is a possibility that seizure may occur at the flange / roller end face contact portion of the tapered roller bearing as used in the prior art. In the case where excessive preload due to sudden acceleration or low-temperature start and lateral acceleration due to turning occur simultaneously, the risk of seizure is further increased. Since the pumping action of a tapered roller bearing is affected by the bearing size, the pumping action becomes stronger for a larger bearing at the same rotational speed. The front side is smaller than the rear side and the pumping action is weak, so the amount of lubrication tends to be insufficient. Accordingly, seizure problems are particularly likely to occur in the front bearing.

In order to solve these problems, there are conventionally the following technologies. Partitions, baffles, seals, etc. are provided before and after the bearing so that oil can be easily retained in the bearing even if the amount of oil supplied to the bearing decreases. (JP-A-8-210472, JP-A-9-1054)
No. 50, JP-A-8-326877). An obstruction piece that inhibits reflux is provided in the return path for the front-side bearing to prevent oil from immediately flowing out of the bearing (Utility Model Registration No. 2604074).

These prior arts are not originally based on the improvement of bearings, and thus have problems such as a need to change the structure of the differential device and an increase in the number of parts such as seals. In addition, in these conventional technologies, the oil retaining ability inside the bearing is improved, but the amount of penetrating oil in the bearing is reduced.
Problems may occur in aspects such as bearing cooling. However,
If the amount of penetrating oil is increased, the ability to retain oil inside the bearing generally decreases, and seizure resistance when the amount of oil supplied to the bearing decreases decreases. It is not easy to improve the amount of oil passing through the bearing and the ability to retain oil in the bearing in a well-balanced manner.

On the other hand, according to the embodiment shown in FIG. 3, the tapered roller bearing 2 is provided along the paths (I) and (II) in the figure.
The lubricating oil supplied to the outer rings 213a and 214 flows into the outer rings 213a and 214 as shown in FIG.
A sufficient lubricating oil amount on the side of the flange portions 213d and 214d of a is secured. When the differential device is started, the outer ring 213
Since the flanges 213d and 214d below the a and 214a function as dams, lubricating oil can be stored in the bearings 213 and 214. Further, even if the supply of the lubricating oil is stopped for some reason during the operation of the bearing, the outer ring 213
The flange portions 213d and 214d of the a and 214a function as dams, and can temporarily hold the lubricating oil in the bearings 213 and 214. Therefore, seizure of the tapered roller bearings 213 and 214 can be effectively prevented regardless of the time of starting / running. It should be noted that a certain effect can be obtained even if the collar portion 213d is provided only on the outer ring 213a of the front bearing 213 which is easily seized.

According to the present embodiment, the load capacity and the like are not different from the conventional tapered roller bearing in which the collar is provided on the inner ring. The operation of assembling the bearing into the device can be performed in almost the same procedure as the conventional tapered roller bearing. The effect can be expected even when applied to a low-speed shaft-side bearing (not shown) that supports the ring gear 204. In addition to the differential device 200, an effect can be expected when applied to a bearing in another automotive gear device (for example, a transmission, a transfer).

When the method of assembling the bearing into the drive unit may be different from that of the conventional tapered roller bearing (for example, at the time of a new design), it may be a separate outer ring collar or a bearing form with an inner ring collar. Although the present invention has been described with reference to a railway vehicle driving device and an automobile differential device as an example, naturally, even if the present invention is applied to a reduction / speed increasing gear device of another driving device, it effectively prevents problems such as seizure caused by poor lubrication. Can be solved. The present invention is also effective when applied not only to the bearing on the high-speed shaft side (corresponding to the drive shaft of the embodiment) of the gear device but also to the bearing on the low-speed shaft side.

[0041]

According to the present invention, lubricating a running bearing by using a tapered roller bearing provided with a flange portion on an outer ring is used as a bearing for a driving device such as a railway vehicle driving device and a car differential device. When the engine stops temporarily or when the system is started, the collar of the outer ring functions as an oil sump. During high-speed running, a sufficient amount of oil can be secured in the collar by centrifugal force. The seizure resistance of the bearing can be improved regardless of running conditions. Further, since only the position of the flange portion is different from that of the conventional tapered roller bearing, the load capacity, size, and the like can be unchanged. Furthermore, the retainer is swaged integrally with the outer ring and rollers, and the inner ring can be separated as a simple conical shape without a flange, so that it can be separated from the conventional tapered roller bearing (inner ring, roller and cage integrated, outer ring can be separated). It is possible to incorporate the bearing into the drive in almost the same way. in addition,
The design change of the bearing peripheral structure of the drive device can also be minimized.

[Brief description of the drawings]

FIG. 1 is a drive device 1 for a railway vehicle including a first embodiment.
It is axial sectional drawing of 00.

FIG. 2 is a diagram showing a comparison result of a sliding speed (V) at a contact portion between a flange portion and an end surface of a configuration in which a flange portion is provided in an inner ring and a configuration in which a flange portion is provided in an outer ring.

FIG. 3 is a cross-sectional view of an automobile differential gear device (hereinafter, a differential device) which is another example of the driving device.

FIG. 4 is a schematic plan view showing a drive mechanism of a railway vehicle.

FIG. 5 is a schematic side view showing a drive mechanism of a railway vehicle.

FIG. 6 is an axial sectional view of a driving device 10 including a small gear 3 and a large gear 4;

7A is a view showing the tapered roller bearing 14 taken out, and FIG. 7B is a view of a part of the tapered roller bearing 14 of FIG. FIG.

FIG. 8 is an axial cross-sectional view of a model of a tapered roller bearing with an inner ring collar including a cage used in an experiment performed by the present inventors.

[Explanation of symbols]

 113, 114, 213, 214 Tapered roller bearings 113a, 114a, 213a, 214a Outer rings 113b, 114b, 213b, 214b Inner rings 113c, 114c, 213c, 214c Rollers 113d, 114d, 213d, 214d Collar portion

Claims (1)

[Claims] 1. An outer ring integrally formed with a flange portion extending inward in a radial direction at at least one end in an axial direction, an inner ring, and a plurality of rollers rotatable between the outer ring and the inner ring. And a bearing device used for a drive device of a vehicle.