JPH0141649Y2 - - Google Patents

Description

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

Conventionally, in this type of bearing device, in order to fix the bearing to the axle, the bearing device portion of the axle is formed into a cylindrical portion 2 having a shoulder portion 1, and the circumference of the end surface A structure in which screw holes 3, 3, 3 are provided at three equal locations on the top, the inner ring is tightly fitted into the cylindrical portion 2, and a front cover 5 is tightened with bolts 6 through a dust ring 4 on the end surface of the inner ring. It was hot.

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, the three tightening bolts 6 are removed, the front cover 5 of the bearing device is removed, and the center hole of the axle is removed.
It was a hassle to install a special cover to expose the bearing and prevent chips and dirt from entering the inside of the bearing during grinding.

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 in order to firmly fix the inner ring to the axle and allow the inner ring's shaft end collar ring to receive thrust loads.
In addition, screws are required on the outer peripheral surface of the end of the axle, making it 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 is attached to the retaining ring 11.
As a result, 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 guidance of the rollers 10 becomes insufficient (the rollers skew), resulting in edge load, etc. occurs,
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. .

It is known that a circumferential groove is formed on the axle in order to fix the inner ring to the axle, and a sliding member is housed in the circumferential groove. (Refer to Japanese Utility Model Application No. 56-127423.) However, since the circumferential groove has a tapered surface on the shaft end side, a sliding member having a tapered surface on the inner surface is used to accommodate the tapered surface. The sliding member has a tapered surface formed on its outer surface to correspond to the tapered surface on the inner surface of the guide member, and since the inner diameter of the sliding member must be smaller than the outer diameter of the shaft end, it cannot be fitted as is. Since this is impossible, the sliding member is divided into a plurality of parts and formed into a fan shape, and each sliding member is provided with internal threads to be screwed into bolts at required locations.

Therefore, it is extremely troublesome to accommodate a plurality of sliding members in the circumferential groove and to screw each bolt into the sliding member through the elongated hole of the guide member fitted on the shaft end side, and it is difficult to tighten the bolts. Therefore, the sliding member slides on the tapered surface and moves in the centripetal and axial directions.As the sliding member moves in the centripetal direction, the bolt also moves in the centripetal direction, so the through hole of the guide member becomes a long hole. Since the guide member also moves in the axial direction, the position of the tapered surface and other dimensions corresponding thereto are required to be controlled in order to control the amount of movement, which is troublesome. .

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 peripheral surface of the outer ring, and the inner ring and the seal ring are attached to the axle. In a roller bearing device for a railway vehicle that is fitted, a circumferential groove having left and right surfaces perpendicular to the axle is carved in the shaft end of the axle, and a retaining ring fitted in the circumferential groove is sandwiched. Insert an inner cover on the shaft end side, fit a collar between it and the seal ring on the opposite shaft end side, and then form a through hole in the inner cover and have multiple screw holes in the collar. After that, a bolt is passed through the through hole of the inner cover and the threaded hole of the collar, and as the bolt is rotated, the vertical wall surface of the inner cover presses the seal ring toward the opposite end of the shaft.

Since the rear end surface of the collar is received by the retaining ring by the above technical means, further rotation of the bolt causes the vertical wall surface of the inner cover to press the seal ring toward the opposite end of the shaft.

As a result, there is no gap between the end face of the inner ring and the front end face of the seal ring, that is, the axial clearance of the rollers remains as it was at the initial stage, and defects that shorten the life of the roller bearing do not occur.

Further, since no screw hole is formed at the shaft end, there is no problem in testing by ultrasonic flaw detection.

Next, an embodiment of the present invention will be described based on FIG.
04 is an inner ring fixed to the axle 105 by interference fit, and 106 and 107 are cages 10, respectively.
Cylindrical roller held and guided by 61, 1071, 10
Reference numeral 8 denotes a seat for seating 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.

a seal body 102 fixed to the outer ring 101;
103, the seal body 102 on the opposite shaft end is attached to the inner ring 1.
04, and is fitted to 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 connected 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 seal ring 110 is located on the shaft end side of the axle 105 and is in contact with the outer circumferential surface of a seal ring 110 that is fitted into the axle 105 .

The collar 114 loosely fitted into the reduced diameter portion 1053 of the axle 105 has a screw hole 1141 formed therein, and the collar 114 fits into the circumferential groove 1 at the end of the axle 105.
It is received by a retaining ring 116 attached to 052.

In addition, the inner cover 117 that is loosely fitted to the reduced diameter portion 1053 of the axle 105 is
7, and an annular cylindrical wall 1172 on the shaft end side. Has a gap,
The inner circumferential surface 1173 is formed with an annular notch that approximately matches the outer diameter of the retaining ring 116, and the outer circumferential surface 11
74 is loosely fitted to the inner circumferential surface 111 of the seal ring 110, and furthermore, a vertical wall surface 1176 is formed in the radial direction of the shaft end side of the outer circumferential surface 1174.

A through hole 1175 for inserting the tightening bolt 115 is provided around the protrusion 1171 on the opposite shaft end of the base.
is formed, and the through hole 1175 is formed at a location that matches the screw hole 1141 of the collar 114.

A band 118 is provided on the outer periphery of the annular cylindrical wall 1172.
Outer cover 119 is fixed via.

The effect will be explained.

The tightening bolt 115 is inserted through the through hole 1175 of the inner cover 117 via the detent 120 and is screwed into the screw hole 1141 of the collar 114 .

Further, the collar 114 retreats in proportion to the rotation of the tightening bolt 115, and when the rear end surface of the collar 114 is received by the retaining ring 116, the tightening bolt 115 pushes the inner cover 117 forward, and the inner cover 117 is pushed forward. The vertical wall surface 1176 of the cover 117 presses the end surface of the seal ring 110 toward the reversed end side, thereby eliminating any gap between the end surface of the inner ring 104 and the seal ring 110.

In addition, the outer periphery of the retaining ring 116 and the inner cover 1
Since there is almost no gap between the retaining ring and the inner circumferential surface 1173 of the retaining ring 17, the diameter of the retaining ring, which is cut at one place on the circumference, is prevented from expanding.

FIG. 4 shows another embodiment of the bearing device of the present invention, which differs from the previous embodiment in that it includes a double row roller bearing using tapered rollers 121 instead of the double row cylindrical roller bearing, and a means for attaching the outer cover. is band 118
A mounting bolt 122 is used instead.

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

In particular, since the circumferential groove formed at the end of the axle of the present invention is a square groove with a surface perpendicular to the axis, the retaining ring fitted into the square groove is generally cut in one place. Moreover, since the collar does not need to fit into the circumferential groove, an annular integral body can be used, and furthermore, it is extremely easy to assemble using bolts inserted into the through holes of the inner cover. At the same time, there is no need for detailed dimensional control as in the above-mentioned known example (Japanese Utility Model Publication No. 127423/1989), so that the present invention has the advantageous effects of further increasing work efficiency.

[Brief explanation of the drawing]

1 and 2 are vertical cross-sectional views of a conventional cylindrical roller bearing device for vehicles, FIG. 3 is a vertical cross-sectional view showing one embodiment of the device of the present invention, and FIG. 4 is another embodiment of the device of the present invention. FIG. 110: Seal ring, 114: Color, 11
6: Retaining ring, 117: Inner cover, 119:
outer cover.

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 onto an axle, circumferential grooves having left and right surfaces perpendicular to the axle are carved in the shaft end of the axle, and the circumferential groove is Insert the inner cover on the shaft end side, sandwiching the retaining ring fitted in the groove, insert the collar between it and the seal ring on the opposite shaft end, and insert a hole through the inner cover and a screw in the collar. A roller bearing device for a railway vehicle axle, characterized in that the vertical wall surface of the inner cover presses the seal ring toward the opposite shaft end side by means of bolts formed through the through holes and screwed into the screw holes. .