WO2015143937A1 - 铁路用密封式圆柱滚子轴承 - Google Patents

铁路用密封式圆柱滚子轴承 Download PDF

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Publication number
WO2015143937A1
WO2015143937A1 PCT/CN2015/070999 CN2015070999W WO2015143937A1 WO 2015143937 A1 WO2015143937 A1 WO 2015143937A1 CN 2015070999 W CN2015070999 W CN 2015070999W WO 2015143937 A1 WO2015143937 A1 WO 2015143937A1
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Prior art keywords
sealing cover
side wall
cylindrical roller
roller bearing
sealed cylindrical
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PCT/CN2015/070999
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English (en)
French (fr)
Inventor
刘鑫
徐镜峰
刘彩芬
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舍弗勒技术股份两合公司
刘鑫
徐镜峰
刘彩芬
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Application filed by 舍弗勒技术股份两合公司, 刘鑫, 徐镜峰, 刘彩芬 filed Critical 舍弗勒技术股份两合公司
Publication of WO2015143937A1 publication Critical patent/WO2015143937A1/zh

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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

Definitions

  • the invention relates to the field of bearings, in particular to a Cylindrical Roller Bearing (CRB) for railways.
  • CB Cylindrical Roller Bearing
  • a conventional sealed cylindrical roller bearing for railway includes: an inner ring 1 having a rib 1a at both ends in the axial direction; an outer ring 2 disposed outside the inner ring 1; Two rows of cylindrical rollers 3 between 1 and the outer ring 2, the cylindrical rollers 3 can move axially with the outer ring 2 relative to the inner ring 1, and when the outer ring 2 is at the intermediate position, each column of cylindrical rollers 3 and adjacent There is an axial gap S between the ribs 1a; an annular sealing cover 4 for sealing the bearing and preventing leakage of lubricant from the inside of the bearing, one circumference of the annular sealing cover 4 is fixed on the outer ring 2, and the other circumference is located in the block. There is a radial gap between the radially outer side of the side 1a and the rib 1a such that the seal achieved by the annular seal 4 is a non-contact seal.
  • the outer ring 2 When the bearing is working, as shown in FIG. 1 and FIG. 2, the outer ring 2 can be moved axially to the left from the intermediate position relative to the inner ring 1 until reaching the left limit position; as shown in FIG. 1 and FIG. 3, the outer ring 2 is also It is possible to move axially to the right from the intermediate position relative to the inner ring 1 until the right extreme position is reached.
  • the axial displacement of sealed cylindrical roller bearings for railways is required to be larger and larger. If the above-described sealed cylindrical roller bearing structure is continuously used, the following problem occurs: as shown in the area A in FIGS. 2 and 3, since the outer ring 2 moves axially relative to the inner ring 1, the outer ring 1 carries The annular sealing cover 4 moves together with respect to the rib 1a, so that when the outer ring 2 moves relative to the inner ring 1 to the left or right limit position, the rib 1a is completely outside the annular sealing cover 4, that is, there is no radial direction between the two.
  • the facing area causes a large gap between the annular seal 4 and the rib 1a, which causes a pumping effect (pumping) Effect), causing lubricant leakage and external pollutants to enter the bearing, thereby reducing the life of the bearing.
  • the problem to be solved by the present invention is that the existing sealed cylindrical roller bearing for railway has a poor sealing effect when the axial displacement of the outer ring is large.
  • the present invention provides a sealed cylindrical roller bearing for railways, comprising:
  • An inner ring having a rib at both ends along the axial direction
  • An outer ring disposed outside the inner ring, and an inner cavity formed between the outer ring and the inner ring;
  • a roller located within the inner cavity and movable axially relative to the inner ring with respect to the inner ring;
  • the second sealing cover has: a first sidewall fixed to an outer circumferential surface of the rib, and a first sidewall spaced apart from the first sidewall and located radially outward of the first sidewall a second sidewall, the radial gap exists between the first sealing cover and the second sidewall.
  • the second sealing cover further has: a bottom wall connecting the first side wall and the second side wall;
  • the first side wall, the second side wall, and the bottom wall collectively define an annular groove surrounding the rib, and an opening of the annular groove faces the roller.
  • the first sealing cover includes a free wall extending to an axially outer side of the bearing and radially between the inner ring and the outer ring, and the free wall and the second side wall are stored In the radial gap.
  • the second sidewall is located radially inward of the free wall.
  • the second sidewall is located radially outward of the free wall.
  • the bottom wall extends in a radial direction and is axially outward of the inner ring.
  • the free wall, the first sidewall, and the second sidewall all extend in the axial direction.
  • the first sidewall is closer to the roller than the second sidewall in the axial direction.
  • the maximum value of the radial gap is greater than 0 and less than or equal to 1 mm.
  • the first sealing cover fixed on the outer ring and the second sealing cover fixed on the rib of the inner ring always have a right area in the radial direction and a radial gap exists Therefore, even in the case of a large axial displacement of the bearing, the non-contact sealing of the bearing can be realized under the joint action of the first sealing cover and the second sealing cover, preventing leakage of the lubricant and entry of external pollutants. Inside the bearing, the bearing life is extended.
  • FIG. 1 is a partial cross-sectional view showing an axial section of an outer ring of a conventional sealed cylindrical roller bearing of the railway;
  • Figure 2 is a partial cross-sectional view taken along the axial section of the outer ring of Figure 1 in the left extreme position;
  • Figure 3 is a partial cross-sectional view taken along the axial section of the outer ring of Figure 1 in the right extreme position;
  • Figure 4 is a partial cross-sectional view, taken along the axial section, of the sealed cylindrical roller bearing for railways with the outer ring in the intermediate position in the first embodiment of the present invention
  • Figure 5 is a partial cross-sectional view taken along the axial section of the outer ring of Figure 4 in the left extreme position;
  • Figure 6 is a partial cross-sectional view taken along the axial section of the outer ring of Figure 4 when it is at the right extreme position;
  • Figure 7 is a partial cross-sectional view showing the axial section of the sealed cylindrical roller bearing for railways in the second extreme position of the second embodiment of the present invention.
  • sealed cylindrical roller bearings for railways include:
  • the inner ring 10 of the rib 11 is provided at both ends of the axial direction;
  • roller 30 located in the inner cavity G and movable together with the outer ring 20 in the axial direction relative to the inner ring 10;
  • the retainer 40 located in the inner cavity G, the retainer 40 is for separating the plurality of rollers 30 in the circumferential direction;
  • the annular second sealing cover 60 is fixed to the rib 11, and the first sealing cover 50 and the second sealing cover 60 seal the inner cavity G on both sides of the inner cavity G.
  • the first sealing cover 50 includes: a free wall 53 extending to the outside of the bearing axial direction and radially between the inner ring 10 and the outer ring 20, the free wall 53 extending in the axial direction; being fixed outside
  • the first fixed wall 51 on the outer circumferential surface of the ring 20 extends in the axial direction; the second fixed wall 52 of the first fixed wall 51 is connected to the free wall 53 and the second fixed wall 52 is fixed outside.
  • the axial end face of the ring 20 extends radially along the bearing. Therefore, in the present embodiment, the longitudinal cross section of the first sealing cover 50 has a zigzag shape. In other words, when the first sealing cover 50 is cut along the axial direction of the bearing, the first sealing cover 50 has a zigzag cross section.
  • the second sealing cover 60 has a first side wall 62 fixed on the outer circumferential surface 110 of the rib 11 , and the first side wall 62 extends in the axial direction; and is spaced apart from the first side wall 62 And a second side wall 63 located radially outward of the first side wall 62, the second side wall 63 extending in the axial direction and being further away from the roller 30 in the axial direction than the first side wall 62; connecting the first side wall 62 And a bottom wall 64 of the second side wall 63, the bottom wall 64 extends in the radial direction and is located axially outward of the inner ring 10.
  • the first side wall 62, the second side wall 63, and the bottom wall 64 collectively enclose an annular groove 61 surrounding the rib 11, and the opening of the annular groove 61 faces the roller 30. Therefore, in the present embodiment, the longitudinal cross section of the second sealing cover 60 is substantially U-shaped.
  • the outer ring 20 When the bearing is in operation, the outer ring 20 will move axially relative to the inner ring 10 with the rollers 30. 4 and 5, the free wall 53 and the first sealing cover 50 are moved in the axial direction relative to the inner ring 10 from the intermediate position to the left extreme position or from the left extreme position to the intermediate position.
  • the second side wall 63 of the second sealing cover 60 always has a facing area in the radial direction and has a radial gap;
  • the second side wall 63 of the second sealing cover 60 always has a right facing area in the radial direction and has a radial gap.
  • the first seal cover 50 and the second seal cover 60 each have a right facing area in the radial direction and a radial gap exists.
  • the technical solution of the embodiment has the following advantages: when the outer ring moves relative to the inner ring in the axial direction, the first sealing cover fixed on the outer ring and the rib fixed on the inner ring
  • the second sealing cover always has a right facing area in the radial direction and has a radial gap, so that the bearing can be realized under the joint action of the first sealing cover and the second sealing cover even in the case of a large axial displacement of the bearing
  • the non-contact seal prevents lubricant leakage and external contaminants from entering the bearing, thus extending the life of the bearing.
  • the shapes of the first sealing cover 50 and the second sealing cover 60 are not limited to the above, as long as the axial movement of the outer ring 20 relative to the inner ring 10 is ensured. At this time, the first seal cover 50 and the second seal cover 60 always have a facing area in the radial direction and a radial gap exists.
  • the radial gap refers to the interval between the portion of the second seal cover 60 that is radially closest to the first seal cover 50 and the first seal cover 50, and the nearest portion is radially opposite the first seal cover 50. Has a right area.
  • the radial clearance between the first seal shroud 50 and the second seal shroud 60 may remain constant along the axial direction of the bearing or may vary along the axial direction of the bearing.
  • the radial gap between the first seal cover 50 and the second seal cover 60 is located radially outward of the outer circumferential surface 110 of the rib 11 and remains unchanged along the axial direction of the bearing.
  • the radial gap is further away from the rib 11 in the radial direction of the bearing, so that the lubricant is less likely to leak, and external contaminants are less likely to enter the bearing, thereby prolonging the life of the bearing.
  • the radial clearance between the first seal shroud 50 and the second seal shroud 60 may also vary along the axial direction of the bearing.
  • 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 less than or equal to 1 mm.
  • the annular groove 61 facing the roller 30 in the second sealing cover 60 by providing the annular groove 61 facing the roller 30 in the second sealing cover 60, the amount of lubricant stored in the bearing is increased, so that the lubricant is not easily removed from the first sealing cover 50 and the second.
  • the radial gap between the seal covers 60 leaks.
  • the annular seal 61 may not be provided in the second sealing cover 60.
  • annular groove surrounding the rib may be disposed in the first sealing cover, and the opening of the annular groove of the first sealing cover faces the roller and communicates with the inner cavity of the bearing.
  • the outer ring 20 can also be located at the left extreme position (shown in FIG. 5 ) or the right extreme position relative to the inner ring 10 ( In the case of FIG. 6, the second side wall 63 is prevented from interfering with the holder 40 while the first side wall 62 of the second seal cover 60 closer to the roller 30 projects into the holder 40.
  • the distance between the first side wall 62 and the second side wall 63 along the axial direction of the inner ring 10 and the roller 30 may also be equal.
  • the first seal cover 50 is fixed to the outer circumferential surface and the axial end surface of the outer ring 20. In other embodiments, the first sealing cover 50 can also be secured to other locations on the outer ring 20.
  • the second sealing cover 60 is fixed to the outer circumferential surface 110 of the rib 11. In other embodiments, the second sealing cover 60 can also be fixed at other locations on the ribs 11.
  • the first sealing cover 50 is interference-fitted with the outer ring 20 such that the first sealing cover 50 is fixed to the outer ring 20.
  • the first sealing cover 50 may be fixed to the outer ring 20 in other manners.
  • the second sealing cover 60 is interference-fitted with the rib 11 so that the second sealing cover 60 is fixed to the rib 11 .
  • the second sealing cover 60 may be fixed to the rib 11 in other manners.
  • the difference between the second embodiment and the first embodiment is the relative positional relationship of the free wall of the first sealing cover and the second side wall of the second sealing cover in the radial direction.
  • the second side wall 63 of the second sealing cover 60 is always located radially inward of the free wall 53 of the first sealing cover 50; and in the second embodiment, reference is made to the drawing. As shown in FIG. 7, the second side wall 63 of the second seal cover 60 is always located radially outward of the free wall 53 of the first seal cover 50.
  • the outer ring 20 moves axially relative to the inner ring 10
  • the free wall 53 of the first sealing cover 50 is always movably located in the annular groove 61 of the second sealing cover 60 such that the first sealing cover 50 and the second sealing cover 60 always have a facing area in the radial direction and exist Radial clearance, thus enabling a non-contact seal of the bearing under the combined action of the first sealing cover and the second sealing cover, even in the case of a large axial displacement of the bearing.
  • the annular seal 61 facing the roller 30 in the second seal cover 60 by providing the annular seal 61 facing the roller 30 in the second seal cover 60, the amount of lubricant stored in the bearing is increased.
  • the embodiments use a progressive writing method, and the differences from the foregoing embodiments are mainly described.
  • the same portions in the respective embodiments can be referred to the foregoing embodiments.

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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

一种铁路用密封式圆柱滚子轴承，包括：沿轴向的两端均设有挡边（11）的内圈（10）；设在所述内圈（10）外的外圈（20），所述外圈（20）和内圈（10）之间形成有内腔（G）；位于所述内腔（G）内并可与所述外圈（20）一起相对所述内圈（10）沿轴向移动的滚子（30）；固设于所述外圈（20）上的环形第一密封罩（50）；固设于所述挡边（11）上的环形第二密封罩（60），所述第一密封罩（50）和第二密封罩（60）在所述内腔（G）轴向两侧密封所述内腔（G），所述外圈（20）相对内圈（10）沿轴向移动时，所述第一密封罩（50）和第二密封罩（60）沿径向始终具有正对面积且存在径向间隙。解决了现有铁路用密封式圆柱滚子轴承在外圈轴向位移较大时密封效果不佳的问题。

Description

铁路用密封式圆柱滚子轴承
本申请要求2014年3月28日提交中国专利局、申请号为201410123959.4、发明名称为“铁路用密封式圆柱滚子轴承”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本发明涉及轴承领域，特别是涉及一种铁路用密封式圆柱滚子轴承(Cylindrical Roller Bearing，简称CRB)。
背景技术
如图1所示，现有一种铁路用密封式圆柱滚子轴承包括：沿轴向的两端均设有挡边1a的内圈1；设在内圈1外的外圈2；位于内圈1和外圈2之间的两列圆柱滚子3，圆柱滚子3可与外圈2一起相对内圈1沿轴向移动，外圈2位于中间位置时，每列圆柱滚子3和邻近的挡边1a之间均存在轴向间隙S；用于密封轴承、防止润滑剂从轴承内部泄漏的环形密封罩4，环形密封罩4的一个周缘固定于外圈2上、另一周缘位于挡边1a的径向外侧并与挡边1a之间存在径向间隙，使得由环形密封罩4实现的密封为非接触式密封。
轴承工作时，结合图1和图2所示，外圈2可以相对内圈1从中间位置沿轴向向左移动，直至到达左极限位置；结合图1和图3所示，外圈2也可以相对内圈1从中间位置沿轴向向右移动，直至到达右极限位置。
随着铁路领域的技术发展，要求铁路用密封式圆柱滚子轴承的轴向位移越来越大。若继续采用上述密封式圆柱滚子轴承结构，会出现以下问题：如图2和图3中的A区域所示，由于外圈2相对内圈1沿轴向移动时，外圈1会带着环形密封罩4一起相对挡边1a移动，故会导致外圈2相对内圈1移动至左极限或右极限位置时，挡边1a完全位于环形密封罩4之外，即两者沿径向无正对面积，造成环形密封罩4与挡边1a之间存在较大间隙，该间隙会引起泵效应(pumping  effect)，致使润滑剂泄漏、以及外界污染物进入轴承内，进而降低轴承的寿命。
发明内容
本发明要解决的问题是：现有铁路用密封式圆柱滚子轴承在外圈轴向位移较大时，密封效果不佳。
为解决上述问题，本发明提供了一种铁路用密封式圆柱滚子轴承，包括：
沿轴向的两端均设有挡边的内圈；
设在所述内圈外的外圈，所述外圈和内圈之间形成有内腔；
位于所述内腔内并可与所述外圈一起相对所述内圈沿轴向移动的滚子；
固设于所述外圈上的环形第一密封罩；
固设于所述挡边上的环形第二密封罩，所述第一密封罩和第二密封罩在所述内腔轴向两侧密封所述内腔，所述外圈相对内圈沿轴向移动时，所述第一密封罩和第二密封罩沿径向始终具有正对面积且存在径向间隙。
可选的，所述第二密封罩具有：固设于所述挡边的外圆周面上的第一侧壁、以及与第一侧壁间隔设置并位于所述第一侧壁径向外侧的第二侧壁，所述第一密封罩与所述第二侧壁之间存在所述径向间隙。
可选的，所述第二密封罩还具有：连接所述第一侧壁和第二侧壁的底壁；
所述第一侧壁、第二侧壁、底壁共同围成环绕所述挡边的环形凹槽，所述环形凹槽的开口面向所述滚子。
可选的，所述第一密封罩包括延伸至轴承轴向外侧并在径向上位于所述内圈和外圈之间的自由壁，所述自由壁与所述第二侧壁之间存 在所述径向间隙。
可选的，所述第二侧壁位于所述自由壁径向内侧。
可选的，所述第二侧壁位于所述自由壁径向外侧。
可选的，所述底壁沿径向延伸并位于所述内圈轴向外侧。
可选的，所述自由壁、第一侧壁、第二侧壁均沿轴向延伸。
可选的，所述第一侧壁沿轴向比第二侧壁更靠近所述滚子。
可选的，所述径向间隙的最大值大于0小于等于1mm。
与现有技术相比，本发明的技术方案具有以下优点：
外圈相对内圈沿轴向移动时，固设于外圈上的第一密封罩和固设于内圈的挡边上的第二密封罩沿径向始终具有正对面积且存在径向间隙，使得即使在轴承具有较大轴向位移的情况下，也能够在第一密封罩和第二密封罩的共同作用下实现轴承的非接触式密封，防止了润滑剂泄漏、以及外界污染物进入轴承内，进而延长了轴承的寿命。
附图说明
图1是现有一种铁路用密封式圆柱滚子轴承的外圈位于中间位置时沿轴向剖面的局部剖面图；
图2是图1中外圈位于左极限位置时沿轴向剖面的局部剖面图；
图3是图1中外圈位于右极限位置时沿轴向剖面的局部剖面图；
图4是本发明的第一实施例中外圈位于中间位置时铁路用密封式圆柱滚子轴承沿轴向剖面的局部剖面图；
图5是图4中外圈位于左极限位置时沿轴向剖面的局部剖面图；
图6是图4中外圈位于右极限位置时沿轴向剖面的局部剖面图；
图7是本发明的第二实施例中外圈位于左极限位置时铁路用密封式圆柱滚子轴承沿轴向剖面的局部剖面图。
具体实施方式
为使本发明的上述目的、特征和优点能够更为明显易懂，下面结合附图对本发明的具体实施例做详细的说明。
第一实施例
如图4所示，铁路用密封式圆柱滚子轴承包括：
沿轴向的两端均设有挡边11的内圈10；
设在内圈10外的外圈20，外圈20和内圈10之间形成有内腔G；
位于内腔G内并可与外圈20一起相对内圈10沿轴向移动的滚子30；
位于内腔G内的保持架40，保持架40用于将多个滚子30沿周向分隔开；
固设于外圈20上的环形第一密封罩50；
固设于挡边11上的环形第二密封罩60，第一密封罩50和第二密封罩60在内腔G轴向两侧密封内腔G。
在本实施例中，第一密封罩50包括：延伸至轴承轴向外侧并在径向上位于内圈10和外圈20之间的自由壁53，自由壁53沿轴向延伸；固设于外圈20的外圆周面上的第一固定壁51，第一固定壁51沿轴向延伸；连接自由壁53与第一固定壁51的第二固定壁52，第二固定壁52固设于外圈20的轴向端面上并沿轴承径向延伸。故在本实施例中，第一密封罩50的纵截面呈Z字形。换言之，沿着轴承的轴线方向切割第一密封罩50时，第一密封罩50的截面呈Z字形。
在本实施例中，第二密封罩60具有：固设于挡边11的外圆周面110上的第一侧壁62，第一侧壁62沿轴向延伸；与第一侧壁62间隔设置并位于第一侧壁62径向外侧的第二侧壁63，第二侧壁63沿轴向延伸，且沿轴向比第一侧壁62更远离滚子30；连接第一侧壁62 和第二侧壁63的底壁64，底壁64沿径向延伸并位于内圈10轴向外侧。第一侧壁62、第二侧壁63、底壁64共同围成环绕挡边11的环形凹槽61，环形凹槽61的开口面向滚子30。故在本实施例中，第二密封罩60的纵截面大体呈U型。
轴承工作时，外圈20会带着滚子30一起相对内圈10沿轴向移动。结合图4和图5所示，外圈20相对内圈10从中间位置向左极限位置或从左极限位置向中间位置沿轴向移动的过程中，第一密封罩50的自由壁53和第二密封罩60的第二侧壁63沿径向始终具有正对面积且存在径向间隙；
结合图4和图6所示，外圈20相对内圈10从中间位置向右极限位置或从右极限位置向中间位置沿轴向移动的过程中，第一密封罩50的自由壁53和第二密封罩60的第二侧壁63沿径向始终具有正对面积且存在径向间隙。
由上述轴承的工作过程可知，在外圈20相对内圈10沿轴向移动至任何位置时，第一密封罩50和第二密封罩60沿径向均具有正对面积且存在径向间隙。
与现有技术相比，本实施例的技术方案具有以下优点：外圈相对内圈沿轴向移动时，固设于外圈上的第一密封罩和固设于内圈的挡边上的第二密封罩沿径向始终具有正对面积且存在径向间隙，使得即使在轴承具有较大轴向位移的情况下，也能够在第一密封罩和第二密封罩的共同作用下实现轴承的非接触式密封，防止了润滑剂泄漏、以及外界污染物进入轴承内，进而延长了轴承的寿命。
需说明的是，在本实施例的技术方案中，第一密封罩50、第二密封罩60的形状均不应仅局限于上面所述，只要保证在外圈20相对内圈10沿轴向移动时，第一密封罩50和第二密封罩60沿径向始终具有正对面积且存在径向间隙即可。
需说明的是，在本发明中，第一密封罩50和第二密封罩60之间 的径向间隙是指：第二密封罩60中沿径向距离第一密封罩50最近的部分与第一密封罩50之间的间隔，所述最近的部分与第一密封罩50沿径向具有正对面积。第一密封罩50和第二密封罩60之间的径向间隙可以沿轴承轴向保持不变，也可以沿轴承轴向变化。具体到本实施例中，第一密封罩50和第二密封罩60之间的径向间隙位于挡边11的外圆周面110的径向外侧，并沿轴承轴向保持不变。
由上述可知，如图4所示，在本实施例中，第一密封罩50和第二密封罩60之间的径向间隙与挡边11的外圆周面110之间存在距离，与现有技术相比，所述径向间隙在轴承径向方向上距离挡边11更远，使得润滑剂更不容易泄漏、外界污染物更不容易进入轴承内，进而能够延长轴承的寿命。
在本实施例中，经研究发现，当第一密封罩50和第二密封罩60之间的径向间隙大于0小于等于1mm时，轴承具有良好的密封效果。
在其他实施例中，第一密封罩50和第二密封罩60之间的径向间隙也可以沿轴承轴向变化。在这种情况下，在第一密封罩50和第二密封罩60之间的最大径向间隙大于0小于等于1mm时，轴承具有良好的密封效果。
在本实施例中，通过在第二密封罩60中设置面向滚子30的环形凹槽61，增大了轴承内的润滑剂储存量，使得润滑剂不容易从第一密封罩50与第二密封罩60之间的径向间隙泄漏。在其他实施例中，第二密封罩60中也可以不设置环形凹槽61。
另外，在本实施例的变换例中，第一密封罩中也可以设置环绕挡边的环形凹槽，第一密封罩的环形凹槽的开口面向滚子并与轴承的内腔连通。通过在第一密封罩中设置上述环形凹槽，同样也可以达到增大轴承内的润滑剂储存量的目的。
在本实施例中，通过使第一侧壁62沿内圈10轴向比第二侧壁63更靠近滚子30，一方面可以将第一侧壁62的更多部分固定在挡边 11上，使得第二密封罩60更为牢靠地固设于挡边11上；另一方面，也可以使得在外圈20相对内圈10位于左极限位置(图5所示)或右极限位置(图6所示)时，在更靠近滚子30的第二密封罩60的第一侧壁62伸入保持架40内的同时，防止了第二侧壁63与保持架40发生干涉。
在其他实施例中，第一侧壁62、第二侧壁63沿内圈10轴向与滚子30之间的距离也可以相等。
在本实施例中，第一密封罩50固设于外圈20的外圆周面和轴向端面上。在其他实施例中，第一密封罩50也可以固设于外圈20上的其他位置。
在本实施例中，第二密封罩60固设于挡边11的外圆周面110上。在其他实施例中，第二密封罩60也可以固设于挡边11上的其他位置。
在本实施例中，第一密封罩50与外圈20过盈配合使得第一密封罩50固设于外圈20上。在其他实施例中，也可以其他方式使第一密封罩50固设于外圈20上。
在本实施例中，第二密封罩60与挡边11过盈配合使得第二密封罩60固设于挡边11上。在其他实施例中，也可以其他方式使第二密封罩60固设于挡边11上。
第二实施例
第二实施例与第一实施例之间的区别在于：第一密封罩的自由壁和第二密封罩的第二侧壁在径向上的相对位置关系。
在第一实施例中，参考图4所示，第二密封罩60的第二侧壁63始终位于第一密封罩50的自由壁53的径向内侧；而在第二实施例中，参考图7所示，第二密封罩60的第二侧壁63始终位于第一密封罩50的自由壁53的径向外侧。
在第二实施例的技术方案中，在外圈20相对内圈10沿轴向移动 时，第一密封罩50的自由壁53始终可移动地位于第二密封罩60的环形凹槽61内，使得第一密封罩50与第二密封罩60沿径向始终具有正对面积且存在径向间隙，因而即使在轴承具有较大轴向位移的情况下，也能够在第一密封罩和第二密封罩的共同作用下实现轴承的非接触式密封。
在本实施例中，通过在第二密封罩60设置面向滚子30的环形凹槽61，增大了轴承内的润滑剂储存量。
本发明中，各实施例采用递进式写法，重点描述与前述实施例的不同之处，各实施例中的相同部分可以参照前述实施例。
虽然本发明披露如上，但本发明并非限定于此。任何本领域技术人员，在不脱离本发明的精神和范围内，均可作各种更动与修改，因此本发明的保护范围应当以权利要求所限定的范围为准。

Claims (10)

  1. 一种铁路用密封式圆柱滚子轴承，包括：
    沿轴向的两端均设有挡边的内圈；
    设在所述内圈外的外圈，所述外圈和内圈之间形成有内腔；
    位于所述内腔内并可与所述外圈一起相对所述内圈沿轴向移动的滚子；
    固设于所述外圈上的环形第一密封罩；
    其特征在于，还包括：固设于所述挡边上的环形第二密封罩，所述第一密封罩和第二密封罩在所述内腔轴向两侧密封所述内腔，所述外圈相对内圈沿轴向移动时，所述第一密封罩和第二密封罩沿径向始终具有正对面积且存在径向间隙。
  2. 如权利要求1所述的铁路用密封式圆柱滚子轴承，其特征在于，所述第二密封罩具有：固设于所述挡边的外圆周面上的第一侧壁、以及与第一侧壁间隔设置并位于所述第一侧壁径向外侧的第二侧壁，所述第一密封罩与所述第二侧壁之间存在所述径向间隙。
  3. 如权利要求2所述的铁路用密封式圆柱滚子轴承，其特征在于，所述第二密封罩还具有：连接所述第一侧壁和第二侧壁的底壁；
    所述第一侧壁、第二侧壁、底壁共同围成环绕所述挡边的环形凹槽，所述环形凹槽的开口面向所述滚子。
  4. 如权利要求3所述的铁路用密封式圆柱滚子轴承，其特征在于，所述第一密封罩包括延伸至轴承轴向外侧并在径向上位于所述内圈和外圈之间的自由壁，所述自由壁与所述第二侧壁之间存在所述径向间隙。
  5. 如权利要求4所述的铁路用密封式圆柱滚子轴承，其特征在于，所述第二侧壁位于所述自由壁径向内侧。
  6. 如权利要求4所述的铁路用密封式圆柱滚子轴承，其特征在于，所述第二侧壁位于所述自由壁径向外侧。
  7. 如权利要求3所述的铁路用密封式圆柱滚子轴承，其特征在 于，所述底壁沿径向延伸并位于所述内圈轴向外侧。
  8. 如权利要求4所述的铁路用密封式圆柱滚子轴承，其特征在于，所述自由壁、第一侧壁、第二侧壁均沿轴向延伸。
  9. 如权利要求8所述的铁路用密封式圆柱滚子轴承，其特征在于，所述第一侧壁沿轴向比第二侧壁更靠近所述滚子。
  10. 如权利要求1所述的铁路用密封式圆柱滚子轴承，其特征在于，所述径向间隙的最大值大于0小于等于1mm。
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