CN104948591B - Sealed cylindrical roller bearing for railway - Google Patents

Sealed cylindrical roller bearing for railway Download PDF

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Publication number
CN104948591B
CN104948591B CN201410123959.4A CN201410123959A CN104948591B CN 104948591 B CN104948591 B CN 104948591B CN 201410123959 A CN201410123959 A CN 201410123959A CN 104948591 B CN104948591 B CN 104948591B
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CN
China
Prior art keywords
side wall
sealing cover
outer ring
radial
inner cavity
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Active
Application number
CN201410123959.4A
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Chinese (zh)
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CN104948591A (en
Inventor
刘鑫
徐镜峰
刘彩芬
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Schaeffler Technologies AG and Co KG
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Schaeffler Technologies AG and Co KG
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Priority to CN201410123959.4A priority Critical patent/CN104948591B/en
Priority to PCT/CN2015/070999 priority patent/WO2015143937A1/en
Publication of CN104948591A publication Critical patent/CN104948591A/en
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Publication of CN104948591B publication Critical patent/CN104948591B/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7889—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to an inner race and extending toward the outer race
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61F—RAIL VEHICLE SUSPENSIONS, e.g. UNDERFRAMES, BOGIES OR ARRANGEMENTS OF WHEEL AXLES; RAIL VEHICLES FOR USE ON TRACKS OF DIFFERENT WIDTH; PREVENTING DERAILING OF RAIL VEHICLES; WHEEL GUARDS, OBSTRUCTION REMOVERS OR THE LIKE FOR RAIL VEHICLES
    • B61F15/00—Axle-boxes
    • B61F15/12—Axle-boxes with roller, needle, or ball bearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61F—RAIL VEHICLE SUSPENSIONS, e.g. UNDERFRAMES, BOGIES OR ARRANGEMENTS OF WHEEL AXLES; RAIL VEHICLES FOR USE ON TRACKS OF DIFFERENT WIDTH; PREVENTING DERAILING OF RAIL VEHICLES; WHEEL GUARDS, OBSTRUCTION REMOVERS OR THE LIKE FOR RAIL VEHICLES
    • B61F15/00—Axle-boxes
    • B61F15/20—Details
    • B61F15/22—Sealing means preventing entrance of dust or leakage of oil
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7816—Details of the sealing or parts thereof, e.g. geometry, material
    • F16C33/782—Details of the sealing or parts thereof, e.g. geometry, material of the sealing region
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/76—Sealings of ball or roller bearings
    • F16C33/78—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members
    • F16C33/7886—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted outside the gap between the inner and outer races, e.g. sealing rings mounted to an end face or outer surface of a race
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
    • F16C19/24—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly
    • F16C19/28—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly with two or more rows of rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2326/00—Articles relating to transporting
    • F16C2326/10—Railway vehicles

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)
  • Sealing Of Bearings (AREA)

Abstract

A sealed cylindrical roller bearing for railways, comprising: the two ends along the axial direction are both provided with inner rings of flanges; the outer ring is arranged outside the inner ring, and an inner cavity is formed between the outer ring and the inner ring; a roller located within the inner cavity and movable with the outer race in an axial direction relative to the inner race; the annular first sealing cover is fixedly arranged on the outer ring; and the first sealing cover and the second sealing cover are fixedly arranged on the flange, the inner cavity is sealed at two axial sides of the inner cavity, and when the outer ring moves relative to the inner ring along the axial direction, the first sealing cover and the second sealing cover always have dead areas along the radial direction and have radial gaps. The problem of current sealed cylindrical roller bearing for railway sealed effect when outer lane axial displacement is great is not good is solved.

Description

Sealed cylindrical roller bearing for railway
Technical Field
The invention relates to the field of bearings, in particular to a sealed Cylindrical Roller Bearing (CRB) for railways.
Background
As shown in fig. 1, a conventional sealed cylindrical roller bearing for railways includes: the inner rings 1 of the flanges 1a are arranged at the two ends along the axial direction; an outer ring 2 arranged outside the inner ring 1; the cylindrical rollers 3 can move axially relative to the inner ring 1 together with the outer ring 2, and when the outer ring 2 is located at the middle position, an axial gap S exists between each row of cylindrical rollers 3 and the adjacent flange 1 a; and an annular seal cover 4 for sealing the bearing and preventing lubricant from leaking from the inside of the bearing, wherein one circumferential edge of the annular seal cover 4 is fixed on the outer ring 2, and the other circumferential edge is positioned at the radial outer side of the rib 1a and has a radial gap with the rib 1a, so that the seal realized by the annular seal cover 4 is a non-contact seal.
When the bearing works, as shown in fig. 1 and fig. 2, the outer ring 2 can move axially leftwards relative to the inner ring 1 from the middle position until reaching a left limit position; as shown in fig. 1 and 3, the outer ring 2 may also be moved axially to the right relative to the inner ring 1 from the intermediate position until the right limit position is reached.
With the technical development in the railway field, the axial displacement of the sealed cylindrical roller bearing for the railway is required to be larger and larger. If the above-mentioned sealed cylindrical roller bearing structure is continuously adopted, the following problems will occur: as shown in area a in fig. 2 and 3, when the outer ring 2 moves axially relative to the inner ring 1, the outer ring 1 carries the annular seal cover 4 to move together with the rib 1a, so that when the outer ring 2 moves to the left limit position or the right limit position relative to the inner ring 1, the rib 1a is completely located outside the annular seal cover 4, that is, there is no facing area between the two in the radial direction, so that there is a large gap between the annular seal cover 4 and the rib 1a, and the gap causes a pumping effect (pumping effect), which causes lubricant leakage and external contaminants to enter the bearing, thereby reducing the service life of the bearing.
Disclosure of Invention
The invention aims to solve the problems that: the existing sealed cylindrical roller bearing for the railway has poor sealing effect when the axial displacement of an outer ring is large.
In order to solve the above problems, the present invention provides a sealed cylindrical roller bearing for railways, comprising:
the two ends along the axial direction are both provided with inner rings of flanges;
the outer ring is arranged outside the inner ring, and an inner cavity is formed between the outer ring and the inner ring;
a roller located within the inner cavity and movable with the outer race in an axial direction relative to the inner race;
the annular first sealing cover is fixedly arranged on the outer ring;
and the first sealing cover and the second sealing cover are fixedly arranged on the flange, the inner cavity is sealed at two axial sides of the inner cavity, and when the outer ring moves relative to the inner ring along the axial direction, the first sealing cover and the second sealing cover always have dead areas along the radial direction and have radial gaps.
Optionally, the second sealing cap has: the sealing structure comprises a first side wall fixedly arranged on the outer circumferential surface of the flange and a second side wall arranged at intervals with the first side wall and located on the radial outer side of the first side wall, and a radial gap is formed between the first sealing cover and the second side wall.
Optionally, the second sealing cover further includes: a bottom wall connecting the first and second side walls;
the first side wall, the second side wall and the bottom wall jointly enclose an annular groove surrounding the rib, and an opening of the annular groove faces the roller.
Optionally, the first seal cover includes a free wall extending to an axially outer side of the bearing and located radially between the inner race and the outer race, and the radial gap exists between the free wall and the second side wall.
Optionally, the second sidewall is located radially inward of the free wall.
Optionally, the second side wall is located radially outward of the free wall.
Optionally, the bottom wall extends radially and is located axially outward of the inner ring.
Optionally, the free wall, the first side wall and the second side wall all extend in the axial direction.
Optionally, the first sidewall is axially closer to the roller than the second sidewall.
Optionally, the maximum value of the radial gap is greater than 0 and less than or equal to 1 mm.
Compared with the prior art, the technical scheme of the invention has the following advantages:
when the outer ring moves relative to the inner ring along the axial direction, the first sealing cover fixedly arranged on the outer ring and the second sealing cover fixedly arranged on the flange of the inner ring always have the opposite area along the radial direction and have radial gaps, so that the non-contact sealing of the bearing can be realized under the combined action of the first sealing cover and the second sealing cover even if the bearing has larger axial displacement, the lubricant is prevented from leaking, external pollutants enter the bearing, and the service life of the bearing is prolonged.
Drawings
FIG. 1 is a partial cross-sectional view in axial section of an outer race of a sealed cylindrical roller bearing for a railway in accordance with the prior art in a neutral position;
FIG. 2 is a partial cross-sectional view taken in axial cross-section of the outer race of FIG. 1 in the left extreme position;
FIG. 3 is a partial cross-sectional view taken in axial cross-section of the outer race of FIG. 1 in the right extreme position;
FIG. 4 is a partial cross sectional view of the sealed cylindrical roller bearing for railway in an axial section with the outer race of the first embodiment of the present invention at the intermediate position;
FIG. 5 is a partial cross-sectional view taken in axial cross-section of the outer race of FIG. 4 in the left extreme position;
FIG. 6 is a partial cross-sectional view taken in axial cross-section of the outer race of FIG. 4 in the right extreme position;
fig. 7 is a partial sectional view of a sealed cylindrical roller bearing for a railway in an axial section with an outer race of a second embodiment of the present invention at a left extreme position.
Detailed Description
In order to make the aforementioned objects, features and advantages of the present invention comprehensible, embodiments accompanied with figures are described in detail below.
First embodiment
As shown in fig. 4, the sealed cylindrical roller bearing for railways includes:
the inner rings 10 of the flanges 11 are arranged at the two ends along the axial direction;
an outer ring 20 arranged outside the inner ring 10, and an inner cavity G is formed between the outer ring 20 and the inner ring 10;
rollers 30 located in the inner chamber G and movable in the axial direction with respect to the inner ring 10 together with the outer ring 20;
a cage 40 located within the cavity G, the cage 40 for circumferentially separating the plurality of rollers 30;
an annular first seal cover 50 fixedly arranged on the outer ring 20;
and the annular second sealing cover 60 is fixedly arranged on the flange 11, and the first sealing cover 50 and the second sealing cover 60 seal the inner cavity G at two axial sides of the inner cavity G.
In the present embodiment, the first seal cap 50 includes: a free wall 53 extending to the bearing axially outward and located between the inner ring 10 and the outer ring 20 in the radial direction, the free wall 53 extending in the axial direction; a first fixing wall 51 fixed to the outer circumferential surface of the outer ring 20, the first fixing wall 51 extending in the axial direction; and a second fixed wall 52 connecting the free wall 53 and the first fixed wall 51, wherein the second fixed wall 52 is fixedly arranged on the axial end face of the outer ring 20 and extends along the radial direction of the bearing. Therefore, in the present embodiment, the first sealing cap 50 has a zigzag longitudinal section. In other words, when the first seal cover 50 is cut along the axial direction of the bearing, the cross section of the first seal cover 50 is zigzag-shaped.
In the present embodiment, the second seal cover 60 includes: a first sidewall 62 fixedly disposed on the outer circumferential surface 110 of the flange 11, the first sidewall 62 extending in the axial direction; a second side wall 63 disposed spaced apart from the first side wall 62 and radially outward of the first side wall 62, the second side wall 63 extending in the axial direction and being axially farther from the roller 30 than the first side wall 62; and a bottom wall 64 connecting the first side wall 62 and the second side wall 63, the bottom wall 64 extending in the radial direction and being located axially outside the inner ring 10. The first side wall 62, the second side wall 63 and the bottom wall 64 together enclose an annular groove 61 surrounding the rib 11, the opening of the annular groove 61 facing the roller 30. Therefore, in the present embodiment, the second seal cover 60 has a substantially U-shaped longitudinal section.
During operation of the bearing, the outer ring 20 will move axially with the rollers 30 relative to the inner ring 10. As shown in fig. 4 and 5, during the axial movement of the outer ring 20 relative to the inner ring 10 from the middle position to the left extreme position or from the left extreme position to the middle position, the free wall 53 of the first seal cover 50 and the second side wall 63 of the second seal cover 60 always have facing areas and a radial clearance in the radial direction;
as shown in fig. 4 and 6, during the axial movement of the outer ring 20 relative to the inner ring 10 from the middle position to the right extreme position or from the right extreme position to the middle position, the free wall 53 of the first seal housing 50 and the second side wall 63 of the second seal housing 60 always have facing areas and a radial clearance in the radial direction.
As can be seen from the operation of the bearing, when the outer ring 20 moves to any position in the axial direction relative to the inner ring 10, the first seal cover 50 and the second seal cover 60 have facing areas in the radial direction and have a radial clearance.
Compared with the prior art, the technical scheme of the embodiment has the following advantages: when the outer ring moves relative to the inner ring along the axial direction, the first sealing cover fixedly arranged on the outer ring and the second sealing cover fixedly arranged on the flange of the inner ring always have the opposite area along the radial direction and have radial gaps, so that the non-contact sealing of the bearing can be realized under the combined action of the first sealing cover and the second sealing cover even if the bearing has larger axial displacement, the lubricant is prevented from leaking, external pollutants enter the bearing, and the service life of the bearing is prolonged.
It should be noted that, in the solution of the present embodiment, the shapes of the first seal cover 50 and the second seal cover 60 are not limited to the above, as long as it is ensured that when the outer ring 20 moves in the axial direction relative to the inner ring 10, the first seal cover 50 and the second seal cover 60 always have facing areas and radial gaps in the radial direction.
Note that, in the present invention, the radial gap between the first seal cover 50 and the second seal cover 60 means: the second seal shroud 60 is spaced from the first seal shroud 50 by a portion thereof which is radially closest to the first seal shroud 50, said closest portion having a diametrically opposed area to the first seal shroud 50. The radial gap between the first seal cover 50 and the second seal cover 60 may be constant in the bearing axial direction or may vary in the bearing axial direction. Specifically in the present embodiment, the radial gap between the first seal housing 50 and the second seal housing 60 is located radially outward of the outer circumferential surface 110 of the flange 11 and remains constant in the axial direction of the bearing.
As can be seen from the above description, in the present embodiment, as shown in fig. 4, the radial gap between the first seal cover 50 and the second seal cover 60 is farther from the outer circumferential surface 110 of the rib 11 in the radial direction of the bearing than in the prior art, so that the lubricant is less likely to leak, the external contaminants are less likely to enter the bearing, and the service life of the bearing can be prolonged.
In the present embodiment, it is found through research that the bearing has a good sealing effect when the radial gap between the first seal cover 50 and the second seal cover 60 is greater than 0 and equal to or less than 1 mm.
In other embodiments, the radial clearance between the first seal shroud 50 and the second seal shroud 60 may also vary axially along the bearing. In this case, the bearing has a good sealing effect when the maximum radial gap between the first seal cover 50 and the second seal cover 60 is greater than 0 and 1mm or less.
In the present embodiment, by providing the annular groove 61 facing the roller 30 in the second seal cover 60, the lubricant storage amount within the bearing is increased, so that the lubricant is less likely to leak from the radial gap between the first seal cover 50 and the second seal cover 60. In other embodiments, the annular groove 61 may not be provided in the second seal housing 60.
In addition, in a modification of the present embodiment, an annular groove surrounding the rib may be provided in the first seal cover, and an opening of the annular groove of the first seal cover faces the roller and communicates with the inner cavity of the bearing. By providing the above-mentioned annular groove in the first seal boot, the same can be achieved with an increased lubricant storage capacity in the bearing.
In the present embodiment, by making the first side wall 62 closer to the roller 30 than the second side wall 63 along the axial direction of the inner ring 10, on the one hand, more parts of the first side wall 62 can be fixed on the rib 11, so that the second seal cover 60 is more firmly fixed on the rib 11; on the other hand, when the outer race 20 is positioned at the left limit position (shown in fig. 5) or the right limit position (shown in fig. 6) with respect to the inner race 10, the first side wall 62 of the second seal cover 60 closer to the rollers 30 is prevented from interfering with the cage 40 while extending into the cage 40.
In other embodiments, the distances between the first and second sidewalls 62 and 63 and the rollers 30 along the axial direction of the inner ring 10 may be equal.
In the present embodiment, the first seal cover 50 is fixedly provided on the outer circumferential surface and the axial end surface of the outer ring 20. In other embodiments, the first seal cover 50 may be fixed at other positions on the outer ring 20.
In this embodiment, the second sealing cover 60 is fixedly disposed on the outer circumferential surface 110 of the flange 11. In other embodiments, the second sealing cover 60 may be fixed at other positions on the rib 11.
In this embodiment, the first seal cover 50 is tightly fitted to the outer ring 20, so that the first seal cover 50 is fixed on the outer ring 20. In other embodiments, the first seal cover 50 may be fixed to the outer ring 20 in other manners.
In this embodiment, the second seal cover 60 is in interference fit with the rib 11, so that the second seal cover 60 is fixedly arranged on the rib 11. In other embodiments, the second sealing cover 60 may be fixed to the rib 11 in other manners.
Second embodiment
The difference between the second embodiment and the first embodiment is that: the free wall of the first seal housing and the second side wall of the second seal housing are in a radially opposed relationship.
In the first embodiment, illustrated with reference to fig. 4, the second side wall 63 of the second containment cap 60 is always radially inside the free wall 53 of the first containment cap 50; in the second embodiment, however, as shown with reference to fig. 7, the second side wall 63 of the second seal housing 60 is always located radially outside the free wall 53 of the first seal housing 50.
In the solution of the second embodiment, when the outer ring 20 moves axially relative to the inner ring 10, the free wall 53 of the first seal cover 50 is always movably located in the annular groove 61 of the second seal cover 60, so that the first seal cover 50 and the second seal cover 60 always have facing areas and radial gaps in the radial direction, and thus, even in the case of a bearing with a large axial displacement, the non-contact sealing of the bearing can be realized under the combined action of the first seal cover and the second seal cover.
In the present embodiment, by providing the annular groove 61 facing the roller 30 in the second seal cover 60, the lubricant storage amount in the bearing is increased.
In the present invention, each embodiment is written in a progressive manner, and the differences from the previous embodiments are emphasized, and the same parts in each embodiment can be referred to the previous embodiments.
Although the present invention is disclosed above, the present invention is not limited thereto. Various changes and modifications may be effected therein by one skilled in the art without departing from the spirit and scope of the invention as defined in the appended claims.

Claims (4)

1. A sealed cylindrical roller bearing for railways, comprising:
the two ends along the axial direction are both provided with inner rings of flanges;
the outer ring is arranged outside the inner ring, and an inner cavity is formed between the outer ring and the inner ring;
a roller located within the inner cavity and movable with the outer race in an axial direction relative to the inner race;
the annular first sealing cover is fixedly arranged on the outer ring;
it is characterized by also comprising: the first sealing cover and the second sealing cover seal the inner cavity at two axial sides of the inner cavity, when the outer ring moves axially relative to the inner ring, the first sealing cover and the second sealing cover always have opposite areas along the radial direction and have radial gaps,
the first seal housing being located entirely radially outwardly of the second seal housing and having an axially extending free wall,
the second seal cover has: a first side wall fixedly arranged on the outer circumferential surface of the flange, a second side wall arranged at an interval with the first side wall and positioned at the radial outer side of the first side wall, and a bottom wall connected with the first side wall and the second side wall and extending along the radial direction, wherein the first side wall, the second side wall and the bottom wall jointly enclose a U-shaped annular groove, and the opening of the annular groove faces the roller,
the radial gap exists between the free wall and the second side wall, and the bottom wall is located axially outside an end face of the rib.
2. A sealed cylindrical roller bearing for railways, comprising:
the two ends along the axial direction are both provided with inner rings of flanges;
the outer ring is arranged outside the inner ring, and an inner cavity is formed between the outer ring and the inner ring;
a roller located within the inner cavity and movable with the outer race in an axial direction relative to the inner race;
the annular first sealing cover is fixedly arranged on the outer ring;
it is characterized by also comprising: the first sealing cover and the second sealing cover seal the inner cavity at two axial sides of the inner cavity, when the outer ring moves axially relative to the inner ring, the first sealing cover and the second sealing cover always have opposite areas along the radial direction and have radial gaps,
the second seal cover has: a first side wall fixedly arranged on the outer circumferential surface of the flange, a second side wall arranged at an interval with the first side wall and positioned at the radial outer side of the first side wall, and a bottom wall connected with the first side wall and the second side wall and extending along the radial direction, wherein the first side wall, the second side wall and the bottom wall jointly enclose a U-shaped annular groove, and the opening of the annular groove faces the roller,
the first seal housing has an axially extending free wall extending into the U-shaped annular groove with the radial gap to the second side wall, the bottom wall being located axially beyond the end face of the rib.
3. The sealed cylindrical roller bearing for railway use of claim 1 or 2, wherein said first side wall is axially closer to said roller than said second side wall.
4. The sealed cylindrical roller bearing for railway use according to claim 1 or 2, wherein the maximum value of the radial clearance is greater than 0 and 1mm or less.
CN201410123959.4A 2014-03-28 2014-03-28 Sealed cylindrical roller bearing for railway Active CN104948591B (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201410123959.4A CN104948591B (en) 2014-03-28 2014-03-28 Sealed cylindrical roller bearing for railway
PCT/CN2015/070999 WO2015143937A1 (en) 2014-03-28 2015-01-19 Sealed cylindrical roller bearing for railway use

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201410123959.4A CN104948591B (en) 2014-03-28 2014-03-28 Sealed cylindrical roller bearing for railway

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CN104948591A CN104948591A (en) 2015-09-30
CN104948591B true CN104948591B (en) 2021-09-21

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CN106481669A (en) * 2016-12-13 2017-03-08 福建省永安轴承有限责任公司 Railway freight-car hub spindle holds sealing ring and the bearing equipped with the sealing ring
DE102019131041A1 (en) * 2019-11-18 2021-05-20 Schaeffler Technologies AG & Co. KG Axle set bearing for a rail vehicle

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US5975533A (en) * 1996-09-13 1999-11-02 Brenco, Incorporated Labyrinth-type seal for railway car journal bearing
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