JPS6327146Y2 - - Google Patents

Description

[Detailed Description of the Invention] The present invention relates to a roller bearing device for an axle of a railway vehicle.

Conventionally, in this type of bearing device, in order to fix the bearing to the axle, as shown in FIG. It has a structure in which screw holes 3, 3, 3 are provided at three equal locations, the inner ring is tightly fitted into the cylindrical part 2, and a front cover 5 is tightened with bolts 6 through a dust ring 4 on the end surface of the inner ring. Ta.

However, in order to ensure the maintenance of the vehicle and the safety of operation, the axles of railway vehicle axle bearing devices are periodically inspected for cracks using ultrasonic flaw detection. Therefore, there was a problem that accurate flaw detection could not be performed if the axle had a screw hole 3.

In addition, in order to reshape the tread of a wheel that has become worn due to operation, remove the three tightening bolts 6, remove the front cover 5 of the bearing device, expose the center hole 7 of the axle, and then reshape the tread. It was troublesome to install a special cover to prevent chips and dirt from entering the inside of the bearing.

In order to eliminate these problems and defects,
No. 20980 and Jitsukō No. 52-27454 are known.

However, all of these structures require a large number of parts to firmly fix the inner ring to the axle and allow the inner ring's shaft-end collar ring to receive thrust loads, and also have screws on the outer peripheral surface of the axle end. It was complicated and expensive.

Therefore, a device designed to facilitate ultrasonic flaw detection and reduce weight is known as Utility Model Application No. 139953/1983. However, as shown in Fig. 2, this structure uses a retaining ring 11 that fits into a circumferential groove carved in the shaft end to prevent the seal ring 9 on the shaft end side from coming off. There is a gap between the side surface of the seal ring 11 and the end surface of the seal ring 9.

Therefore, during use, the seal ring 9 loosens toward the retaining ring 11, and the gap between the inner ring spacer 12 and the seal ring 9, that is, the groove width a, becomes larger than the initial value, and the rollers 10 are not guided sufficiently. (The rollers are skewed.) This causes edge loading, etc.
The life of the roller bearing will be significantly reduced.

In short, since the rollers 10 and inner ring spacer 12 are manufactured to have appropriate values for the inner ring groove width dimension, it is not desirable for bearing performance to have a gap between the end face of the inner ring 8 and the end face 13 of the seal ring 9. .

The technical problem of the present invention is to not form a tightening bolt hole at the shaft end in order to facilitate ultra-high frequency flaw detection, and to avoid creating a gap between the end face of the inner ring and the end face of the seal ring.

The structure of the present invention, that is, the technical means for solving the above technical problem is as follows.

The outer ring has an outer ring, an inner ring, and a double row of roller rows, and the outer ring has a seal body that seals the bearing at both ends thereof, and a seal ring that slides on the outer circumferential surface of the outer ring, and the inner ring and the seal ring are attached to the axle. In the roller bearing device for a railway vehicle that is fitted, a circumferential groove is carved in the shaft end of the axle, and a collar is fitted and inserted between the retaining ring fitted in the circumferential groove and the seal ring on the shaft end side. A plurality of screw holes are formed around the collar, a bolt is passed through the screw hole, and as the bolt advances, the tip presses the seal ring toward the opposite end of the shaft.

With the above technical means, the front end surface of the seal ring is pressed toward the opposite shaft end by the advancement of the bolt, and at the same time, the collar into which the bolt is screwed is received by the retaining ring, so that the end surface of the inner ring and the seal ring are There is no gap between the front end faces, that is, the axial clearance of the rollers remains as it was at the beginning, and defects that shorten the life of the roller bearing do not occur.Also, since there are no screw holes formed on the shaft end, ultrasonic flaw detection is possible. It does not cause any hindrance to the inspection by.

Next, an embodiment of the present invention will be described based on FIGS. 3 and 4. Reference numeral 101 denotes an outer ring having seal bodies 102 and 103 fixed to the inner surfaces of both ends thereof for sealing the bearing, and 104 a ring that fits onto the axle 105. Inner rings 106 and 107, which are fixed by a fit, are cylindrical rollers held and guided by cages 1061 and 1071, respectively, and 108 is a saddle that sits on the outer ring 101.

The outer ring 101 has a fixed collar 111 that guides the cylindrical rollers 106, 107 only in the center of its inner circumferential surface and receives a thrust load at the same time, and has no ribs formed on either end side.

In addition, the inner ring 104 has the cylindrical roller 1 on the opposite end side.
The inner ring 10 guides the 07 and receives thrust load.
4, a seal ring 110 on the shaft end side, and a roller guide ring 11 at a position facing the fixed collar 111 of the outer ring 101.
2.

The thrust load applied to the inner ring 104 toward the shaft end causes the groove width of the roller row between the fixed collar 111 of the outer ring and the fixed collar 113 of the inner ring 104 to be larger than the groove width of the roller row on the shaft end side. Make it smaller,
It is received by the cylindrical rollers 107 of the roller row on the opposite end side.

FIG. 3 shows a first embodiment of the bearing device of the present invention, in which a seal body 102 fixed to an outer ring 101,
103, the seal body 102 on the opposite shaft end is attached to the inner ring 1.
04, and is fitted onto the axle 105, and is in contact with the stepped portion 1051 of the axle 105 and the end surface of the fixed collar 113 of the inner ring 104, and is attached to the axle 105 toward the shaft end. It is in contact with the outer peripheral surface of a seal ring 109 that transmits the applied thrust load to the inner ring 104, and the seal bodies 102, 10
3, the seal body 103 on the shaft end side is connected to the inner ring 104.
The collar 11 is positioned on the shaft end side of the axle 105 and fitted loosely into the reduced diameter portion 1053 of the axle 105.
4 and the collar 114 are connected to the circumferential groove 1 at the end of the axle 105.
Retaining ring 116 attached to 052 and the collar 11
Bolt 1 screwed into screw hole 1141 formed in 4
15, 115, . . . is in contact with the outer peripheral surface of the seal ring 110, which is pressed toward the opposite end of the shaft.

The end surface of the sealing 110 in contact with the inner ring 104 forms a guide surface for the cylindrical rollers 106 on the shaft end side.

Holes 117, 117 formed in the heads of the bolts 115, 115... are hung with locking wires.

The effect will be explained.

The seal ring is pushed toward the opposite end of the shaft by the advancing bolt, which prevents a gap from forming between the end face of the inner ring and the end face of the seal ring. .

The outer ring has a fixed collar in its center that guides the rollers and receives the thrust load, and the inner ring has a fixed collar that guides the rollers on the opposite end of the shaft and receives the thrust load. is guided by the end face of the sealing and the end face of the seal ring.

Furthermore, since there is almost no gap between the outer periphery of the retaining ring and the bolt, the diameter of the retaining ring, which is cut at one point on the circumference, is prevented from expanding.

FIG. 4 shows another embodiment of the device of the present invention, and the general structure is the same as that of the previous embodiment except that the inner cover 118 and the outer cover 122 are attached to the collar 114 on the shaft end side. ，
104 and cylindrical roller 106 and collar 114
The same numbers are used for the same numbers, and the explanation thereof will be omitted.

The inner cover 118 attached to the shaft end side is
The inner cover 118 is composed of an annular protrusion on the opposite shaft end side of the base portion and an annular cylindrical wall 1182 on the shaft end side, and the end surface of the opposite shaft end side projection portion of the base portion of the inner cover 118 is in contact with the back surface of the collar 114, An annular notch 1181 approximately matching the outer diameter of the retaining ring 116 is formed on its inner circumferential surface, and its outer circumferential surface is loosely fitted to the inner circumferential surface of the seal ring 110. It is in contact with the end surface of the seal ring 110.

1183 is a through hole formed in the protrusion of the inner cover 118, which is connected to the screw hole 1102 of the seal ring 110 and the through hole 1142 of the collar 114.
and are formed at locations corresponding to the screw holes 1143 of the collar 114, respectively.

When installing the inner cover 118, the cover mounting bolts 120 inserted into the through holes 1183 are fastened to the screw holes 1102 of the seal ring 110 through the through holes 1142 of the collar 114, so that the inner cover 118 is attached to the seal ring 110. Fixed.

Further, when the mounting bolt 115 inserted through the other through hole 1183 is screwed into the threaded hole 1143 of the collar 114, the tip of the mounting bolt 115 comes into contact with the end surface of the seal ring 110, so that the collar 114 is attached to the retaining ring 116. Contact stops.

Further, an outer cover 122 is attached to the end surface of the cylindrical wall 182 of the inner cover 118 via bolts 123.

With the above configuration, the inner cover 118
Since the inner diameter of the retaining ring 116 approximately matches the outer diameter of the retaining ring 116,
It is possible to prevent the retaining ring from expanding.

FIG. 5 shows another embodiment of the bearing device of the present invention, which differs from the first embodiment in that the double-row tapered roller bearing uses tapered rollers 109 instead of the double-row cylindrical roller bearing.

Since the other parts are the same as those in the first embodiment, the same reference numerals are given and the explanation thereof will be omitted.

[Brief explanation of the drawing]

1 and 2 are longitudinal sectional views of a conventional cylindrical roller bearing device for vehicles, FIG. 3 is a longitudinal sectional view showing an embodiment of the device of the present invention, and FIGS. 4 and 5 are longitudinal sectional views of the device of the present invention. FIG. 7 is a vertical cross-sectional view showing another embodiment. 114...Color, 115...Volt, 116
……Retaining ring.

Claims (1)

[Scope of utility model registration request] It has an outer ring, an inner ring, and a double row of roller rows, the outer ring is provided with a seal body for sealing the bearing at both ends thereof, and a seal ring that slides in contact with the inner circumferential surface of the seal body is disposed on both end faces of the inner ring. In addition, in a roller bearing device for a railway vehicle in which the inner ring and the seal ring are fitted to an axle, a circumferential groove is carved in the shaft end of the axle, and a retaining ring fitted in the circumferential groove and a shaft end side are provided. A collar is inserted between the seal ring and a plurality of screw holes are formed around the collar, a bolt is passed through the screw hole, and as the bolt advances, the tip of the bolt touches the seal ring on the opposite shaft end. A roller bearing device for an axle of a railway vehicle, characterized in that it is pressed against the roller bearing device.