WO2015143937A1 - Roulement à rouleaux cylindrique étanche pour utilisation ferroviaire - Google Patents

Roulement à rouleaux cylindrique étanche pour utilisation ferroviaire Download PDF

Info

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
Authority
WO
WIPO (PCT)
Prior art keywords
sealing cover
side wall
cylindrical roller
roller bearing
sealed cylindrical
Prior art date
Application number
PCT/CN2015/070999
Other languages
English (en)
Chinese (zh)
Inventor
刘鑫
徐镜峰
刘彩芬
Original Assignee
舍弗勒技术股份两合公司
刘鑫
徐镜峰
刘彩芬
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
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/fr

Links

Images

Classifications

    • 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.

Landscapes

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

Abstract

L'invention concerne un roulement à rouleaux cylindrique étanche pour une utilisation ferroviaire comprenant: une bague interne (10) équipée de façon axiale d'une bride (11) au niveau des deux extrémités; une bague externe (20) disposée à l'extérieur de la bague interne (10), une cavité interne (G) étant formée entre la bague externe (20) et la bague interne (10); un rouleau (30) situé dans la cavité interne (G) et pouvant se déplacer de façon axiale conjointement avec la bague externe (20) par rapport à la bague interne (10); un premier couvercle d'étanchéité annulaire (50) fixé sur la bague externe (20); un second couvercle d'étanchéité annulaire (60) fixé sur la bride (11), le premier couvercle d'étanchéité (50) et le second couvercle d'étanchéité (60) assurant l'étanchéité de la cavité interne (G) de façon axiale au niveau de deux côtés de la cavité interne (G), et lorsque la bague externe (20) se déplace de façon axiale par rapport à la bague interne (10), le premier couvercle d'étanchéité (50) et le second couvercle d'étanchéité (60) présentant toujours une zone orientée directement dans la direction radiale et un espace radial. L'invention permet de résoudre le problème de mauvaise étanchéité rencontré lorsque le déplacement axial de la bague externe est relativement important dans les roulements à rouleaux cylindrique étanches existants pour une utilisation ferroviaire.
PCT/CN2015/070999 2014-03-28 2015-01-19 Roulement à rouleaux cylindrique étanche pour utilisation ferroviaire WO2015143937A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201410123959.4 2014-03-28
CN201410123959.4A CN104948591B (zh) 2014-03-28 2014-03-28 铁路用密封式圆柱滚子轴承

Publications (1)

Publication Number Publication Date
WO2015143937A1 true WO2015143937A1 (fr) 2015-10-01

Family

ID=54163529

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2015/070999 WO2015143937A1 (fr) 2014-03-28 2015-01-19 Roulement à rouleaux cylindrique étanche pour utilisation ferroviaire

Country Status (2)

Country Link
CN (1) CN104948591B (fr)
WO (1) WO2015143937A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019131041A1 (de) * 2019-11-18 2021-05-20 Schaeffler Technologies AG & Co. KG Radsatzlager für ein Schienenfahrzeug

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106481669A (zh) * 2016-12-13 2017-03-08 福建省永安轴承有限责任公司 铁路货车轮毂轴承密封圈及装有该密封圈的轴承

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3628837A (en) * 1969-11-21 1971-12-21 Timken Co Bearing assembly having flexible labyrinth enclosures
US5975533A (en) * 1996-09-13 1999-11-02 Brenco, Incorporated Labyrinth-type seal for railway car journal bearing
DE102006045487A1 (de) * 2006-09-27 2008-04-03 Aktiebolaget Skf Lageranordnung
CN102859217A (zh) * 2010-04-08 2013-01-02 Ntn株式会社 铁道车辆的车轴用轴承装置
CN103016515A (zh) * 2011-09-22 2013-04-03 阿母斯替德铁路公司 滚柱轴承密封件
CN102042333B (zh) * 2009-10-13 2013-08-14 阿母斯替德铁路公司 滚子轴承密封件

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3396975A (en) * 1966-03-18 1968-08-13 Timken Roller Bearing Co Bearing seal case construction
JP3779044B2 (ja) * 1997-09-17 2006-05-24 Ｎｔｎ株式会社 鉄道車両用車軸軸受ユニット
JP2006316884A (ja) * 2005-05-12 2006-11-24 Ntn Corp 密封装置付き軸受
US7607836B2 (en) * 2007-03-16 2009-10-27 Amsted Rail Company, Inc Seal for railway car journal bearing
CN203067533U (zh) * 2012-11-28 2013-07-17 洛阳Lyc轴承有限公司 轨道车辆用轴箱轴承

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3628837A (en) * 1969-11-21 1971-12-21 Timken Co Bearing assembly having flexible labyrinth enclosures
US5975533A (en) * 1996-09-13 1999-11-02 Brenco, Incorporated Labyrinth-type seal for railway car journal bearing
DE102006045487A1 (de) * 2006-09-27 2008-04-03 Aktiebolaget Skf Lageranordnung
CN102042333B (zh) * 2009-10-13 2013-08-14 阿母斯替德铁路公司 滚子轴承密封件
CN102859217A (zh) * 2010-04-08 2013-01-02 Ntn株式会社 铁道车辆的车轴用轴承装置
CN103016515A (zh) * 2011-09-22 2013-04-03 阿母斯替德铁路公司 滚柱轴承密封件

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019131041A1 (de) * 2019-11-18 2021-05-20 Schaeffler Technologies AG & Co. KG Radsatzlager für ein Schienenfahrzeug

Also Published As

Publication number Publication date
CN104948591A (zh) 2015-09-30
CN104948591B (zh) 2021-09-21

Similar Documents

Publication Publication Date Title
KR102413732B1 (ko) 밀봉 장치
EP2639468B1 (fr) Unité de palier à contact de roulement
CN104806643B (zh) 铁路用密封式圆柱滚子轴承
CN102422036B (zh) 密封的球面滚柱轴承组件
WO2016188400A1 (fr) Palier
ITTO20130800A1 (it) Unità di tenuta, in particolare per cuscinetti di rotolamento
US10208802B2 (en) Sealing device
WO2015143937A1 (fr) Roulement à rouleaux cylindrique étanche pour utilisation ferroviaire
CN204533223U (zh) 轴承密封结构及其密封圈
US9458937B2 (en) Shaft seal assembly with exclusion pump dust lip
CN204114150U (zh) 密封装置
WO2009060715A1 (fr) Palier pour alternateur
US9644679B2 (en) Slewing bearing, in particular for a vehicle
JPH06651Y2 (ja) 転がり軸受の密封装置
JP2008082392A (ja) 鉄道車両車軸用軸受装置
CN109958719B (zh) 具有接触式密封结构的轴承
US20200292082A1 (en) Sealing device
JP2009281547A (ja) 密封型転がり軸受
JP2016023727A (ja) 転がり軸受の密封装置及び転がり軸受
JP5181794B2 (ja) 転がり軸受装置
JP2016080017A (ja) 車輪支持軸受用密封装置
JP2008157370A (ja) フォロア軸受
JP2016070306A (ja) 密封型転がり軸受
KR101725660B1 (ko) 구름베어링용 씰
JP2005076749A (ja) 密封装置

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 15769323

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase
122 Ep: pct application non-entry in european phase

Ref document number: 15769323

Country of ref document: EP

Kind code of ref document: A1