WO2017069225A1 - Sealed roller bearing and belt-type continuously-variable transmission - Google Patents
Sealed roller bearing and belt-type continuously-variable transmission Download PDFInfo
- Publication number
- WO2017069225A1 WO2017069225A1 PCT/JP2016/081209 JP2016081209W WO2017069225A1 WO 2017069225 A1 WO2017069225 A1 WO 2017069225A1 JP 2016081209 W JP2016081209 W JP 2016081209W WO 2017069225 A1 WO2017069225 A1 WO 2017069225A1
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- Prior art keywords
- seal
- inner ring
- bearing
- lip
- raceway surface
- Prior art date
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Classifications
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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
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
- F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
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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
- F16C33/7816—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
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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
- F16C33/784—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race
- F16C33/7843—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc
- F16C33/7846—Sealings of ball or roller bearings with a diaphragm, disc, or ring, with or without resilient members mounted to a groove in the inner surface of the outer race and extending toward the inner race with a single annular sealing disc with a gap between the annular disc and the inner race
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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
- F16C33/80—Labyrinth sealings
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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
- F16C2361/00—Apparatus or articles in engineering in general
- F16C2361/63—Gears with belts and pulleys
Definitions
- the present invention relates to a rolling bearing with a seal and a belt type continuously variable transmission in which a rolling bearing with a seal is used.
- an outer ring having an outer ring raceway surface on an inner peripheral surface, an inner ring having an inner ring raceway surface on an outer peripheral surface, and a plurality of rollers arranged so as to be able to roll between the outer ring raceway surface and the inner ring raceway surface
- a pair of seal members fixed to both ends in the axial direction of the outer ring, and a sealed type rolling bearing in which the seal member contacts the seal groove of the inner ring is known (for example, see Patent Document 1). ).
- the present invention has been made in view of the above-described problems, and the object thereof is to suppress the intrusion of foreign matters and prevent a decrease in bearing life without incurring an increase in size and efficiency of the bearing.
- Another object of the present invention is to provide a roller bearing with a seal and a belt type continuously variable transmission.
- An outer ring having an outer ring raceway surface on an inner peripheral surface, an inner ring having an inner ring raceway surface on an outer peripheral surface, and a plurality of rolling elements arranged to be freely rollable between the outer ring raceway surface and the inner ring raceway surface; And a seal mounted on the axial end of the outer ring, the seal being in non-contact with the inner ring, and the gap between the seal and the inner ring being set to 0.05 mm to 0.6 mm A rolling bearing with a seal.
- the seal groove is formed at the axial end of the outer peripheral surface of the inner ring, and the axially outer side surface of the seal groove is formed as an inclined surface extending outward in the axial direction and radially outward.
- the seal is in non-contact with the inner ring, and the gap between the seal and the inner ring is set to 0.05 mm to 0.6 mm, so that the foreign matter can be prevented without increasing the size and efficiency of the bearing. Can be prevented from decreasing the bearing life.
- the rotational speed is limited due to heat generated by the sliding resistance of the contact portion.
- the seal is non-contact and can be used at the same rotational speed as when opened. There is also an advantage in terms of allowable rotational speed with respect to the contact seal.
- the rolling bearing 10 with a seal includes an outer ring 11 having an outer ring raceway surface 11a on an inner peripheral surface, an inner ring 12 having an inner ring raceway surface 12a on an outer peripheral surface, and an outer ring raceway surface 11a.
- a plurality of balls (rolling elements) 13 that are rotatably arranged between the inner ring raceway surface 12a, a cage 14 that holds the plurality of balls 13 at substantially equal intervals in the circumferential direction, and both axial ends of the outer ring 11 And an inner ring rotating bearing in which the inner ring 12 rotates.
- the rolling bearing 10 with seal is used in a position where the belt type continuously variable transmission for automobile is not directly lubricated from the belt type continuously variable transmission for automobile and the pump.
- seal mounting grooves 11b for mounting the seal 20 are formed at both ends in the axial direction of the inner peripheral surface of the outer ring 11, respectively. Further, seal grooves 12b are formed at both axial ends of the outer peripheral surface of the inner ring 12 respectively.
- the seal 20 is formed by coating a cored bar 21 obtained by processing a single annular plate into a required shape and covering an elastic material 22 such as rubber or elastomer. It is formed in an annular plate shape. Further, the seal 20 is supported and fixed to the axial end portion of the inner peripheral surface of the outer ring 11 by fitting the outer peripheral edge portion thereof to the seal mounting groove 11 b of the outer ring 11.
- a seal lip 23 extending radially inward is formed at the radially inner end of the elastic member 22 of the seal 20.
- the seal lip portion 23 extends inward in the axial direction, extends inwardly in the inner ring 12 and does not contact the inner ring 12, and extends inward in the radial direction, and intermediate lip 25 in contact with the seal groove 12 b of the inner ring 12.
- the intermediate lip 25 includes a first lip 25a that extends obliquely toward the outside in the axial direction and radially inward, and a second lip 25b that extends toward the inside in the axial direction.
- the gap C in the radial direction of the gap space B1 with the bottom surface 12d of 12b and the gap C in the axial direction of the gap space C1 between the second lip 25b of the intermediate lip 25 and the side surface 12e on the axially inner side of the seal groove 12b are 0. .05mm to 0.6mm respectively.
- the gaps A to C are more preferably set to 0.05 mm to 0.4 mm. Further, the gaps A to C are set so as to satisfy the relations of the gap A> the gap B and the gap A> the gap C.
- a first labyrinth space 27 to be fastened is formed.
- the first labyrinth space 27 is provided between the gap space B1 and the gap space C1 in the labyrinth structure.
- seal groove 12b is formed between the axially outer side surfaces of the first lip 25a and the neck portion 25c of the intermediate lip 25, the inner peripheral surface between the intermediate lip 25 and the outer lip 26, and the axially inner side surface of the outer lip 26.
- a second labyrinth space 28 that holds foreign matter is formed opposite to the side surface 12f on the outer side in the axial direction.
- the second labyrinth space 28 is provided between the gap space A1 and the gap space B1 in the labyrinth structure.
- the second labyrinth space 28 is set to be larger than the first labyrinth space 27. Specifically, the second labyrinth space 28 is 2 to 6 times the first labyrinth space 27, preferably 3 It is set to double to 5 times.
- the axially outer side surface 12f of the seal groove 12b is formed as an inclined surface extending outward in the axial direction and outward in the radial direction. Further, a second labyrinth space 28 of the seal lip portion 23 is disposed to be opened on the radial outer side of the side surface 12f on the axially outer side of the seal groove 12b.
- the seal 20 is not in contact with the inner ring 12, and the outer peripheral lip 26 of the seal lip 23 of the seal 20 and the outer peripheral surface of the shoulder of the seal groove 12b. 12c, a gap B between the first lip 25a of the intermediate lip 25 and the bottom surface 12d of the seal groove 12b, and a gap C between the second lip 25b of the intermediate lip 25 and the side surface 12e on the axially inner side of the seal groove 12b.
- it since it is set to 0.05 mm to 0.6 mm, it is possible to suppress the intrusion of foreign matters and suppress a decrease in bearing life without causing an increase in size and efficiency of the bearing.
- the rotational speed is limited due to heat generated by the sliding resistance of the contact portion.
- the seal is non-contact and can be used at the same rotational speed as when opened. There is also an advantage in terms of allowable rotational speed with respect to the contact seal.
- the rolling bearing 10 with a seal of this embodiment since the axially outer side surface 12f of the seal groove 12b is formed as an inclined surface extending outward in the axial direction and radially outward, the rotation of the inner ring 12 is performed.
- the foreign matter is discharged by the centrifugal force generated by this, and the foreign matter is retained in the second labyrinth space 28 of the seal lip portion 23, so that the intrusion of the foreign matter can be suppressed, thereby further suppressing the deterioration of the bearing life. .
- the seal attachment groove 11b of the outer ring 11 and the seal groove 12b of the inner ring 12 may be formed by cutting and then subjected to grinding. Thereby, the shape and position accuracy of each groove are improved, and the seal gap can be set with high accuracy.
- the seal 20 of the present invention only needs to be attached at least to the axial end portion on the upstream side of the bearing into which the lubricating oil flows, and the downstream axial end portion from which the lubricating oil flows out has other structures. A structure without a seal or a seal may be employed.
- rolling bearings of Reference Example 1, Examples 1 to 7 and Comparative Examples 1 to 5 shown in Table 1 below were prepared, and a rotation test was performed on each of them to determine the bearing life. And the bearing torque was confirmed.
- the rolling bearing one having the same configuration as the rolling bearing shown in FIG. 1 was used, the seal gaps A and B were set constant, and only the setting of the gap C was changed.
- Comparative Examples 1 to 3 since the bearing life is x and the bearing torque is ⁇ , it is possible to suppress a decrease in bearing efficiency, but it is not possible to suppress a decrease in bearing life. I understood it. Further, in Comparative Examples 4 and 5, since the bearing life is ⁇ and the bearing torque is x, it is understood that although the decrease in the bearing life can be suppressed, the decrease in the bearing efficiency cannot be suppressed. It was.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
- Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
- Transmissions By Endless Flexible Members (AREA)
Abstract
Provided are a sealed roller bearing and a belt-type continuously-variable transmission, which are capable of inhibiting entry of foreign matter so as to impede reduction in bearing service life without incurring any dimensional increase or efficiency reduction to the bearing. The present invention is provided with: an outer ring (11) having an outer ring raceway surface (11a) on the inner peripheral surface thereof; an inner ring (12) having an inner ring raceway surface (12a) on the outer peripheral surface thereof; a plurality of rolling elements (13) which are disposed so as to be rollable between the outer ring raceway surface (11a) and the inner ring raceway surface (12a); and a seal (20) that is mounted to an axial end of the outer ring, wherein the seal (20) is not in contact with the inner ring (12), and gaps (A-C) separating the seal (20) from the inner ring (12) are each set to 0.05-0.6 mm.
Description
本発明は、シール付き転がり軸受及びシール付き転がり軸受が使用されたベルト式無段変速機に関する。
The present invention relates to a rolling bearing with a seal and a belt type continuously variable transmission in which a rolling bearing with a seal is used.
従来のシール付き転がり軸受として、内周面に外輪軌道面を有する外輪と、外周面に内輪軌道面を有する内輪と、外輪軌道面と内輪軌道面との間に転動自在に配置される複数の玉と、外輪の軸方向両端部に固定される一対のシール部材と、を備え、シール部材が内輪のシール溝に接触する密封型転がり軸受が知られている（例えば、特許文献１参照。）。
As a conventional rolling bearing with a seal, an outer ring having an outer ring raceway surface on an inner peripheral surface, an inner ring having an inner ring raceway surface on an outer peripheral surface, and a plurality of rollers arranged so as to be able to roll between the outer ring raceway surface and the inner ring raceway surface And a pair of seal members fixed to both ends in the axial direction of the outer ring, and a sealed type rolling bearing in which the seal member contacts the seal groove of the inner ring is known (for example, see Patent Document 1). ).
ところで、自動車用変速機は、燃費向上の点から、軸受に対して小型化・高効率化の要求が高くなってきている。しかし、変速機の内部には、バリの脱落や摩耗粉等の異物が存在しており、その異物が軸受寿命の低下を引き起こしている。また、効率を重視してオープン型軸受とした場合、異物による軸受寿命の低下が懸念されるため、軸受サイズを大きくする（軸受寿命に余裕を持たせる）必要がある。また、小型化を重視して上記特許文献１のような密封型転がり軸受とした場合、接触シール（通常、シール部材とシール溝との締め代は０．０５ｍｍ～０．５０ｍｍ程度）により効率が低下する課題があった。
By the way, the demand for miniaturization and high efficiency of the bearings for automobiles is increasing from the viewpoint of improving fuel efficiency. However, foreign matters such as burrs fall off and wear powder are present inside the transmission, and the foreign matters cause a reduction in bearing life. In addition, when an open type bearing is made with emphasis on efficiency, there is a concern that the bearing life may be reduced due to foreign matter, so it is necessary to increase the bearing size (allowing a margin in the bearing life). In the case of a sealed type rolling bearing as described in Patent Document 1 with an emphasis on downsizing, the contact seal (usually the tightening allowance between the seal member and the seal groove is about 0.05 mm to 0.50 mm) increases the efficiency. There was a problem to be reduced.
本発明は、前述した課題に鑑みてなされたものであり、その目的は、軸受の大型化・低効率化を招くことなく、異物の侵入を抑制して、軸受寿命の低下を抑制することができるシール付き転がり軸受及びベルト式無段変速機を提供することにある。
The present invention has been made in view of the above-described problems, and the object thereof is to suppress the intrusion of foreign matters and prevent a decrease in bearing life without incurring an increase in size and efficiency of the bearing. Another object of the present invention is to provide a roller bearing with a seal and a belt type continuously variable transmission.
本発明の上記目的は、下記の構成により達成される。
（１）内周面に外輪軌道面を有する外輪と、外周面に内輪軌道面を有する内輪と、外輪軌道面と内輪軌道面との間に転動自在に配置される複数の転動体と、外輪の軸方向端部に取り付けられるシールと、を備えるシール付き転がり軸受であって、シールは、内輪と非接触であり、シールと内輪との隙間が、０．０５ｍｍ～０．６ｍｍに設定されることを特徴とするシール付き転がり軸受。
（２）内輪の外周面の軸方向端部にシール溝が形成され、シール溝の軸方向外側の側面が、軸方向外側且つ径方向外側に向かって延びる傾斜面に形成されることを特徴とする（１）に記載のシール付き転がり軸受。
（３）シールの径方向内端部にシールリップ部が形成され、シールリップ部は、異物を留めるラビリンス空間を有することを特徴とする（１）又は（２）に記載のシール付き転がり軸受。
（４）自動車用ベルト式無段変速機で使用される（１）～（３）のいずれか１つに記載のシール付き転がり軸受を使用したベルト式無段変速機。 The above object of the present invention can be achieved by the following constitution.
(1) An outer ring having an outer ring raceway surface on an inner peripheral surface, an inner ring having an inner ring raceway surface on an outer peripheral surface, and a plurality of rolling elements arranged to be freely rollable between the outer ring raceway surface and the inner ring raceway surface; And a seal mounted on the axial end of the outer ring, the seal being in non-contact with the inner ring, and the gap between the seal and the inner ring being set to 0.05 mm to 0.6 mm A rolling bearing with a seal.
(2) The seal groove is formed at the axial end of the outer peripheral surface of the inner ring, and the axially outer side surface of the seal groove is formed as an inclined surface extending outward in the axial direction and radially outward. The rolling bearing with seal according to (1).
(3) The rolling bearing with a seal according to (1) or (2), wherein a seal lip portion is formed at a radially inner end portion of the seal, and the seal lip portion has a labyrinth space for retaining foreign matter.
(4) A belt-type continuously variable transmission using the sealed rolling bearing according to any one of (1) to (3), which is used in a belt-type continuously variable transmission for automobiles.
（１）内周面に外輪軌道面を有する外輪と、外周面に内輪軌道面を有する内輪と、外輪軌道面と内輪軌道面との間に転動自在に配置される複数の転動体と、外輪の軸方向端部に取り付けられるシールと、を備えるシール付き転がり軸受であって、シールは、内輪と非接触であり、シールと内輪との隙間が、０．０５ｍｍ～０．６ｍｍに設定されることを特徴とするシール付き転がり軸受。
（２）内輪の外周面の軸方向端部にシール溝が形成され、シール溝の軸方向外側の側面が、軸方向外側且つ径方向外側に向かって延びる傾斜面に形成されることを特徴とする（１）に記載のシール付き転がり軸受。
（３）シールの径方向内端部にシールリップ部が形成され、シールリップ部は、異物を留めるラビリンス空間を有することを特徴とする（１）又は（２）に記載のシール付き転がり軸受。
（４）自動車用ベルト式無段変速機で使用される（１）～（３）のいずれか１つに記載のシール付き転がり軸受を使用したベルト式無段変速機。 The above object of the present invention can be achieved by the following constitution.
(1) An outer ring having an outer ring raceway surface on an inner peripheral surface, an inner ring having an inner ring raceway surface on an outer peripheral surface, and a plurality of rolling elements arranged to be freely rollable between the outer ring raceway surface and the inner ring raceway surface; And a seal mounted on the axial end of the outer ring, the seal being in non-contact with the inner ring, and the gap between the seal and the inner ring being set to 0.05 mm to 0.6 mm A rolling bearing with a seal.
(2) The seal groove is formed at the axial end of the outer peripheral surface of the inner ring, and the axially outer side surface of the seal groove is formed as an inclined surface extending outward in the axial direction and radially outward. The rolling bearing with seal according to (1).
(3) The rolling bearing with a seal according to (1) or (2), wherein a seal lip portion is formed at a radially inner end portion of the seal, and the seal lip portion has a labyrinth space for retaining foreign matter.
(4) A belt-type continuously variable transmission using the sealed rolling bearing according to any one of (1) to (3), which is used in a belt-type continuously variable transmission for automobiles.
本発明によれば、シールが内輪と非接触であり、シールと内輪との隙間が、０．０５ｍｍ～０．６ｍｍに設定されるため、軸受の大型化・低効率化を招くことなく、異物の侵入を抑制して、軸受寿命の低下を抑制することができる。また、接触シールの場合は、接触部の摺動抵抗による発熱等により回転速度に制限が発生するが、本発明では、シールが非接触であるため、オープン時と同等の回転速度で使用可能であり、接触シールに対して許容回転速度の面でも利点がある。
According to the present invention, the seal is in non-contact with the inner ring, and the gap between the seal and the inner ring is set to 0.05 mm to 0.6 mm, so that the foreign matter can be prevented without increasing the size and efficiency of the bearing. Can be prevented from decreasing the bearing life. In the case of a contact seal, the rotational speed is limited due to heat generated by the sliding resistance of the contact portion. However, in the present invention, the seal is non-contact and can be used at the same rotational speed as when opened. There is also an advantage in terms of allowable rotational speed with respect to the contact seal.
以下、本発明に係るシール付き転がり軸受の一実施形態について、図面に基づいて詳細に説明する。
Hereinafter, an embodiment of a rolling bearing with a seal according to the present invention will be described in detail based on the drawings.
本実施形態のシール付き転がり軸受１０は、図１に示すように、内周面に外輪軌道面１１ａを有する外輪１１と、外周面に内輪軌道面１２ａを有する内輪１２と、外輪軌道面１１ａと内輪軌道面１２ａとの間に転動自在に配置される複数の玉（転動体）１３と、複数の玉１３を周方向に略等間隔に保持する保持器１４と、外輪１１の軸方向両端部にそれぞれ取り付けられるシール２０と、を備え、内輪１２が回転する内輪回転の軸受である。
As shown in FIG. 1, the rolling bearing 10 with a seal according to this embodiment includes an outer ring 11 having an outer ring raceway surface 11a on an inner peripheral surface, an inner ring 12 having an inner ring raceway surface 12a on an outer peripheral surface, and an outer ring raceway surface 11a. A plurality of balls (rolling elements) 13 that are rotatably arranged between the inner ring raceway surface 12a, a cage 14 that holds the plurality of balls 13 at substantially equal intervals in the circumferential direction, and both axial ends of the outer ring 11 And an inner ring rotating bearing in which the inner ring 12 rotates.
また、シール付き転がり軸受１０は、自動車用ベルト式無段変速機において、自動車用ベルト式無段変速機及びポンプから直接潤滑されない位置で使用される。
Also, the rolling bearing 10 with seal is used in a position where the belt type continuously variable transmission for automobile is not directly lubricated from the belt type continuously variable transmission for automobile and the pump.
また、外輪１１の内周面の軸方向両端部には、シール２０を取り付けるためのシール取付溝１１ｂがそれぞれ形成されている。また、内輪１２の外周面の軸方向両端部には、シール溝１２ｂがそれぞれ形成されている。
Further, seal mounting grooves 11b for mounting the seal 20 are formed at both ends in the axial direction of the inner peripheral surface of the outer ring 11, respectively. Further, seal grooves 12b are formed at both axial ends of the outer peripheral surface of the inner ring 12 respectively.
シール２０は、図１に示すように、一枚の円環板状体を所要の形状に加工してなる芯金２１に、ゴムやエラストマー等の弾性材２２を被覆して成形され、全体が円環板状に形成されている。また、シール２０は、その外周縁部を外輪１１のシール取付溝１１ｂに嵌合することによって、外輪１１の内周面の軸方向端部に支持固定される。
As shown in FIG. 1, the seal 20 is formed by coating a cored bar 21 obtained by processing a single annular plate into a required shape and covering an elastic material 22 such as rubber or elastomer. It is formed in an annular plate shape. Further, the seal 20 is supported and fixed to the axial end portion of the inner peripheral surface of the outer ring 11 by fitting the outer peripheral edge portion thereof to the seal mounting groove 11 b of the outer ring 11.
シール２０の弾性材２２の径方向内端部には、径方向内側に延びるシールリップ部２３が形成されている。このシールリップ部２３は、図２に示すように、軸方向内側に延び、内輪１２と非接触の内側リップ２４と、径方向内側に延び、内輪１２のシール溝１２ｂと非接触の中間リップ２５と、中間リップ２５より軸方向外側に位置し、径方向内側に延びて、内輪１２の外周面と非接触の外側リップ２６と、を有し、内輪１２との間でラビリンス構造を形成している。従って、シール２０は、内輪１２に対して非接触である。
A seal lip 23 extending radially inward is formed at the radially inner end of the elastic member 22 of the seal 20. As shown in FIG. 2, the seal lip portion 23 extends inward in the axial direction, extends inwardly in the inner ring 12 and does not contact the inner ring 12, and extends inward in the radial direction, and intermediate lip 25 in contact with the seal groove 12 b of the inner ring 12. And an axially outer side of the intermediate lip 25, extending radially inward, and having an outer peripheral surface of the inner ring 12 and a non-contact outer lip 26, and forming a labyrinth structure with the inner ring 12 Yes. Therefore, the seal 20 is not in contact with the inner ring 12.
中間リップ２５は、軸方向外側且つ径方向内側に向かって斜めに延びる第１リップ２５ａと、軸方向内側に向かって延びる第２リップ２５ｂと、を有する。
The intermediate lip 25 includes a first lip 25a that extends obliquely toward the outside in the axial direction and radially inward, and a second lip 25b that extends toward the inside in the axial direction.
そして、図２に示すように、シールリップ部２３の外側リップ２６とシール溝１２ｂの肩部外周面１２ｃとの隙間空間Ａ１の径方向の隙間Ａ、中間リップ２５の第１リップ２５ａとシール溝１２ｂの底面１２ｄとの隙間空間Ｂ１の径方向の隙間Ｂ、及び中間リップ２５の第２リップ２５ｂとシール溝１２ｂの軸方向内側の側面１２ｅとの隙間空間Ｃ１の軸方向の隙間Ｃが、０．０５ｍｍ～０．６ｍｍにそれぞれ設定されている。また、この隙間Ａ～Ｃは、０．０５ｍｍ～０．４ｍｍに設定されていた方がより好ましい。さらに、隙間Ａ～Ｃは、隙間Ａ＞隙間Ｂ、且つ、隙間Ａ＞隙間Ｃの関係を満たすように設定されている。
As shown in FIG. 2, the gap A in the radial direction of the gap space A1 between the outer lip 26 of the seal lip 23 and the shoulder outer peripheral surface 12c of the seal groove 12b, the first lip 25a of the intermediate lip 25 and the seal groove The gap C in the radial direction of the gap space B1 with the bottom surface 12d of 12b and the gap C in the axial direction of the gap space C1 between the second lip 25b of the intermediate lip 25 and the side surface 12e on the axially inner side of the seal groove 12b are 0. .05mm to 0.6mm respectively. The gaps A to C are more preferably set to 0.05 mm to 0.4 mm. Further, the gaps A to C are set so as to satisfy the relations of the gap A> the gap B and the gap A> the gap C.
また、中間リップ２５の第１リップ２５ａの軸方向内側面と第２リップ２５ｂの内周面との間には、シール溝１２ｂの軸方向内側の側面１２ｅ及び底面１２ｄと対向して、異物を留める第１ラビリンス空間２７が形成されている。第１ラビリンス空間２７は、ラビリンス構造における隙間空間Ｂ１と隙間空間Ｃ１との間に設けられる。
Further, between the axially inner side surface of the first lip 25a of the intermediate lip 25 and the inner peripheral surface of the second lip 25b, the foreign matter is opposed to the side surface 12e and the bottom surface 12d on the axially inner side of the seal groove 12b. A first labyrinth space 27 to be fastened is formed. The first labyrinth space 27 is provided between the gap space B1 and the gap space C1 in the labyrinth structure.
また、中間リップ２５の第１リップ２５ａ及び首部２５ｃの軸方向外側面、中間リップ２５及び外側リップ２６間の内周面、及び外側リップ２６の軸方向内側面との間には、シール溝１２ｂの軸方向外側の側面１２ｆと対向して、異物を留める第２ラビリンス空間２８が形成されている。第２ラビリンス空間２８は、ラビリンス構造における隙間空間Ａ１と隙間空間Ｂ１との間に設けられる。
Further, the seal groove 12b is formed between the axially outer side surfaces of the first lip 25a and the neck portion 25c of the intermediate lip 25, the inner peripheral surface between the intermediate lip 25 and the outer lip 26, and the axially inner side surface of the outer lip 26. A second labyrinth space 28 that holds foreign matter is formed opposite to the side surface 12f on the outer side in the axial direction. The second labyrinth space 28 is provided between the gap space A1 and the gap space B1 in the labyrinth structure.
そして、第２ラビリンス空間２８は、第１ラビリンス空間２７よりも大きく設定されており、具体的には、第２ラビリンス空間２８は、第１ラビリンス空間２７の２倍～６倍、好ましくは、３倍～５倍に設定されている。
The second labyrinth space 28 is set to be larger than the first labyrinth space 27. Specifically, the second labyrinth space 28 is 2 to 6 times the first labyrinth space 27, preferably 3 It is set to double to 5 times.
また、シール溝１２ｂの軸方向外側の側面１２ｆが、軸方向外側且つ径方向外側に向かって延びる傾斜面に形成されている。さらに、このシール溝１２ｂの軸方向外側の側面１２ｆの径方向外側に、シールリップ部２３の第２ラビリンス空間２８が開口して配置されている。
Also, the axially outer side surface 12f of the seal groove 12b is formed as an inclined surface extending outward in the axial direction and outward in the radial direction. Further, a second labyrinth space 28 of the seal lip portion 23 is disposed to be opened on the radial outer side of the side surface 12f on the axially outer side of the seal groove 12b.
以上説明したように、本実施形態のシール付き転がり軸受１０によれば、シール２０が内輪１２と非接触であり、シール２０のシールリップ部２３の外側リップ２６とシール溝１２ｂの肩部外周面１２ｃとの隙間Ａ、中間リップ２５の第１リップ２５ａとシール溝１２ｂの底面１２ｄとの隙間Ｂ、及び中間リップ２５の第２リップ２５ｂとシール溝１２ｂの軸方向内側の側面１２ｅとの隙間Ｃが、０．０５ｍｍ～０．６ｍｍにそれぞれ設定されるため、軸受の大型化・低効率化を招くことなく、異物の侵入を抑制して、軸受寿命の低下を抑制することができる。また、接触シールの場合は、接触部の摺動抵抗による発熱等により回転速度に制限が発生するが、本発明では、シールが非接触であるため、オープン時と同等の回転速度で使用可能であり、接触シールに対して許容回転速度の面でも利点がある。
As described above, according to the rolling bearing 10 with a seal of this embodiment, the seal 20 is not in contact with the inner ring 12, and the outer peripheral lip 26 of the seal lip 23 of the seal 20 and the outer peripheral surface of the shoulder of the seal groove 12b. 12c, a gap B between the first lip 25a of the intermediate lip 25 and the bottom surface 12d of the seal groove 12b, and a gap C between the second lip 25b of the intermediate lip 25 and the side surface 12e on the axially inner side of the seal groove 12b. However, since it is set to 0.05 mm to 0.6 mm, it is possible to suppress the intrusion of foreign matters and suppress a decrease in bearing life without causing an increase in size and efficiency of the bearing. In the case of a contact seal, the rotational speed is limited due to heat generated by the sliding resistance of the contact portion. However, in the present invention, the seal is non-contact and can be used at the same rotational speed as when opened. There is also an advantage in terms of allowable rotational speed with respect to the contact seal.
また、本実施形態のシール付き転がり軸受１０によれば、シール溝１２ｂの軸方向外側の側面１２ｆが、軸方向外側且つ径方向外側に向かって延びる傾斜面に形成されるため、内輪１２の回転による遠心力によって異物を排出し、シールリップ部２３の第２ラビリンス空間２８に異物を滞留させて、異物の侵入を抑制することができ、これにより、軸受寿命の低下を更に抑制することができる。
Moreover, according to the rolling bearing 10 with a seal of this embodiment, since the axially outer side surface 12f of the seal groove 12b is formed as an inclined surface extending outward in the axial direction and radially outward, the rotation of the inner ring 12 is performed. The foreign matter is discharged by the centrifugal force generated by this, and the foreign matter is retained in the second labyrinth space 28 of the seal lip portion 23, so that the intrusion of the foreign matter can be suppressed, thereby further suppressing the deterioration of the bearing life. .
なお、本発明は上記実施形態に例示したものに限定されるものではなく、本発明の要旨を逸脱しない範囲において適宜変更可能である。
例えば、外輪１１のシール取付溝１１ｂと内輪１２のシール溝１２ｂを、それぞれ切削加工により形成した後、研削加工を施してもよい。これにより、各溝の形状及び位置精度が向上して、シール隙間を精度良く設定することができる。
また、本発明のシール２０は、少なくとも潤滑油が流入する軸受の上流側の軸方向端部に取り付けられていればよく、潤滑油が流出する下流側の軸方向端部は、他の構造のシール又はシールを設けない構成とすることもできる。 In addition, this invention is not limited to what was illustrated to the said embodiment, In the range which does not deviate from the summary of this invention, it can change suitably.
For example, the seal attachment groove 11b of theouter ring 11 and the seal groove 12b of the inner ring 12 may be formed by cutting and then subjected to grinding. Thereby, the shape and position accuracy of each groove are improved, and the seal gap can be set with high accuracy.
Further, theseal 20 of the present invention only needs to be attached at least to the axial end portion on the upstream side of the bearing into which the lubricating oil flows, and the downstream axial end portion from which the lubricating oil flows out has other structures. A structure without a seal or a seal may be employed.
例えば、外輪１１のシール取付溝１１ｂと内輪１２のシール溝１２ｂを、それぞれ切削加工により形成した後、研削加工を施してもよい。これにより、各溝の形状及び位置精度が向上して、シール隙間を精度良く設定することができる。
また、本発明のシール２０は、少なくとも潤滑油が流入する軸受の上流側の軸方向端部に取り付けられていればよく、潤滑油が流出する下流側の軸方向端部は、他の構造のシール又はシールを設けない構成とすることもできる。 In addition, this invention is not limited to what was illustrated to the said embodiment, In the range which does not deviate from the summary of this invention, it can change suitably.
For example, the seal attachment groove 11b of the
Further, the
本発明の作用効果を確認するため、下記表１に示す参考例１、実施例１～７、及び比較例１～５の転がり軸受を作成して、それぞれに対して回転試験を行い、軸受寿命と軸受トルクを確認した。転がり軸受については、図１に示す転がり軸受と同構成のものを使用し、シールの隙間Ａ、Ｂを一定に設定し、隙間Ｃの設定のみを変更した。
In order to confirm the effects of the present invention, rolling bearings of Reference Example 1, Examples 1 to 7 and Comparative Examples 1 to 5 shown in Table 1 below were prepared, and a rotation test was performed on each of them to determine the bearing life. And the bearing torque was confirmed. As the rolling bearing, one having the same configuration as the rolling bearing shown in FIG. 1 was used, the seal gaps A and B were set constant, and only the setting of the gap C was changed.
なお、軸受寿命において、〇は、要求される寿命を満たし、◎は、要求される寿命を十分に満たし、×は、要求される寿命を満たさないことを意味する。また、軸受トルクにおいて、〇は、要求される低トルクを満たし、◎は、要求される低トルクを十分に満たし、×は、要求される低トルクを満たさないことを意味する。
In the bearing life, “◯” indicates that the required life is satisfied, “十分” indicates that the required life is sufficiently satisfied, and “x” indicates that the required life is not satisfied. Further, in the bearing torque, O means that the required low torque is satisfied, A means that the required low torque is sufficiently satisfied, and X means that the required low torque is not satisfied.
（軸受寿命の条件）
軸受：６０１３相当（内径φ６５ｍｍ×外径φ１００ｍｍ×幅１８ｍｍ）
荷重：０．３８Ｃｒ
回転数：２０００ｍｉｎ－１
潤滑油：ＣＶＴフルード
混入異物：硬さＨｖ８００の鉄系粉（粒径１５０μｍ～２００μｍ）
潤滑油中に１８０ｐｐｍ混入
（軸受トルクの条件）
軸受：６０１３相当（内径φ６５ｍｍ×外径φ１００ｍｍ×幅１８ｍｍ）
荷重：０．１Ｃｒ
回転数：１５００ｍｉｎ－１
潤滑油：ＣＶＴフルード (Conditions for bearing life)
Bearing: Equivalent to 6013 (inner diameter φ65mm x outer diameter φ100mm x width 18mm)
Load: 0.38Cr
Rotation speed: 2000min-1
Lubricating oil: CVT fluid Contaminated foreign matter: Iron-based powder having a hardness of Hv800 (particle size 150 μm to 200 μm)
180ppm mixed in lubricating oil (bearing torque condition)
Bearing: Equivalent to 6013 (inner diameter φ65mm x outer diameter φ100mm x width 18mm)
Load: 0.1Cr
Rotation speed: 1500min-1
Lubricant: CVT fluid
軸受：６０１３相当（内径φ６５ｍｍ×外径φ１００ｍｍ×幅１８ｍｍ）
荷重：０．３８Ｃｒ
回転数：２０００ｍｉｎ－１
潤滑油：ＣＶＴフルード
混入異物：硬さＨｖ８００の鉄系粉（粒径１５０μｍ～２００μｍ）
潤滑油中に１８０ｐｐｍ混入
（軸受トルクの条件）
軸受：６０１３相当（内径φ６５ｍｍ×外径φ１００ｍｍ×幅１８ｍｍ）
荷重：０．１Ｃｒ
回転数：１５００ｍｉｎ－１
潤滑油：ＣＶＴフルード (Conditions for bearing life)
Bearing: Equivalent to 6013 (inner diameter φ65mm x outer diameter φ100mm x width 18mm)
Load: 0.38Cr
Rotation speed: 2000min-1
Lubricating oil: CVT fluid Contaminated foreign matter: Iron-based powder having a hardness of Hv800 (particle size 150 μm to 200 μm)
180ppm mixed in lubricating oil (bearing torque condition)
Bearing: Equivalent to 6013 (inner diameter φ65mm x outer diameter φ100mm x width 18mm)
Load: 0.1Cr
Rotation speed: 1500min-1
Lubricant: CVT fluid
表１から明らかなように、実施例１～７（隙間寸法が０．０５ｍｍ～０．６ｍｍ）の場合、軸受寿命が◎又は○で、軸受トルクが全て◎であることから、軸受寿命の低下を抑制することができると共に、軸受の効率低下を抑制することができるとわかった。さらに、実施例１～５（隙間寸法が０．０５ｍｍ～０．４ｍｍ）の場合、軸受寿命が全て◎であることから、軸受寿命の低下をより効果的に抑制することができるとわかった。
As is clear from Table 1, in Examples 1 to 7 (gap size is 0.05 mm to 0.6 mm), the bearing life is ◎ or 、 and the bearing torque is all ◎, so the bearing life is reduced. It has been found that it is possible to suppress the decrease in the efficiency of the bearing. Further, in Examples 1 to 5 (gap size is 0.05 mm to 0.4 mm), since the bearing life is all ◎, it was found that the reduction of the bearing life can be more effectively suppressed.
これに対して、比較例１～３の場合、軸受寿命が×で、軸受トルクが◎であることから、軸受の効率低下を抑制することができるものの、軸受寿命の低下を抑制することができないことがわかった。また、比較例４、５の場合、軸受寿命が◎で、軸受トルクが×であることから、軸受寿命の低下を抑制することができるものの、軸受の効率低下を抑制することができないことがわかった。
On the other hand, in Comparative Examples 1 to 3, since the bearing life is x and the bearing torque is 、, it is possible to suppress a decrease in bearing efficiency, but it is not possible to suppress a decrease in bearing life. I understood it. Further, in Comparative Examples 4 and 5, since the bearing life is ◎ and the bearing torque is x, it is understood that although the decrease in the bearing life can be suppressed, the decrease in the bearing efficiency cannot be suppressed. It was.
また、参考例１の場合、軸受寿命が◎で、軸受トルクが○であることから、軸受寿命の低下を抑制することができるものの、軸受の効率低下を抑制する効果が若干低くなることがわかった。これは、外輪と内輪との微小相対変位により、シールリップ部の中間リップの第２リップと内輪とが締め代を有した状態で摺接してしまい、軸受トルクが僅かに上昇してしまうためと考えられる。
Further, in the case of Reference Example 1, since the bearing life is 軸 受 and the bearing torque is 低下, it is possible to suppress the decrease in the bearing life, but the effect of suppressing the decrease in the bearing efficiency is slightly reduced. It was. This is because, due to minute relative displacement between the outer ring and the inner ring, the second lip of the intermediate lip of the seal lip and the inner ring are in sliding contact with a tightening margin, and the bearing torque slightly increases. Conceivable.
以上、本発明を詳細にまた特定の実施態様を参照して説明したが、本発明の精神と範囲を逸脱することなく様々な変更や修正を加えることができることは当業者にとって明らかである。本出願は、２０１５年１０月２３日出願の日本特許出願（特願２０１５－２０９２９７）に基づくものであり、その内容はここに参照として取り込まれる。
While the present invention has been described in detail and with reference to specific embodiments, it will be apparent to those skilled in the art that various changes and modifications can be made without departing from the spirit and scope of the invention. This application is based on a Japanese patent application filed on October 23, 2015 (Japanese Patent Application No. 2015-209297), the contents of which are incorporated herein by reference.
１０ シール付き転がり軸受
１１ 外輪
１１ａ 外輪軌道面
１２ 内輪
１２ａ 内輪軌道面
１２ｂ シール溝
１２ｃ 肩部外周面
１２ｄ シール溝の底面
１２ｅ シール溝の軸方向内側の側面
１２ｆ シール溝の軸方向外側の側面
１３ 玉（転動体）
２０ シール
２１ 芯金
２２ 弾性材
２３ シールリップ部
２４ 内側リップ
２５ 中間リップ
２５ａ 第１リップ
２５ｂ 第２リップ
２６ 外側リップ
２７ 第１ラビリンス空間
２８ 第２ラビリンス空間
Ａ 隙間
Ｂ 隙間
Ｃ 隙間 DESCRIPTION OFSYMBOLS 10 Rolling bearing with seal 11 Outer ring 11a Outer ring raceway surface 12 Inner ring 12a Inner ring raceway surface 12b Seal groove 12c Shoulder outer peripheral surface 12d Seal groove bottom surface 12e Axial inner side surface 12f Seal groove axially outer side surface 13 Ball (Rolling body)
20seal 21 core metal 22 elastic material 23 seal lip portion 24 inner lip 25 intermediate lip 25a first lip 25b second lip 26 outer lip 27 first labyrinth space 28 second labyrinth space A gap B gap C gap
１１ 外輪
１１ａ 外輪軌道面
１２ 内輪
１２ａ 内輪軌道面
１２ｂ シール溝
１２ｃ 肩部外周面
１２ｄ シール溝の底面
１２ｅ シール溝の軸方向内側の側面
１２ｆ シール溝の軸方向外側の側面
１３ 玉（転動体）
２０ シール
２１ 芯金
２２ 弾性材
２３ シールリップ部
２４ 内側リップ
２５ 中間リップ
２５ａ 第１リップ
２５ｂ 第２リップ
２６ 外側リップ
２７ 第１ラビリンス空間
２８ 第２ラビリンス空間
Ａ 隙間
Ｂ 隙間
Ｃ 隙間 DESCRIPTION OF
20
Claims (4)
- 内周面に外輪軌道面を有する外輪と、外周面に内輪軌道面を有する内輪と、前記外輪軌道面と前記内輪軌道面との間に転動自在に配置される複数の転動体と、前記外輪の軸方向端部に取り付けられるシールと、を備えるシール付き転がり軸受であって、
前記シールは、前記内輪と非接触であり、
前記シールと前記内輪との隙間が、０．０５ｍｍ～０．６ｍｍに設定されることを特徴とするシール付き転がり軸受。 An outer ring having an outer ring raceway surface on an inner peripheral surface, an inner ring having an inner ring raceway surface on an outer peripheral surface, and a plurality of rolling elements arranged to be freely rollable between the outer ring raceway surface and the inner ring raceway surface, A seal mounted on the axial end of the outer ring, and a rolling bearing with a seal,
The seal is in non-contact with the inner ring;
A rolling bearing with a seal, wherein a gap between the seal and the inner ring is set to 0.05 mm to 0.6 mm. - 前記内輪の外周面の軸方向端部にシール溝が形成され、
前記シール溝の軸方向外側の側面が、軸方向外側且つ径方向外側に向かって延びる傾斜面に形成されることを特徴とする請求項１に記載のシール付き転がり軸受。 A seal groove is formed at the axial end of the outer peripheral surface of the inner ring,
2. The rolling bearing with a seal according to claim 1, wherein a side surface on the outer side in the axial direction of the seal groove is formed as an inclined surface extending outward in the axial direction and outward in the radial direction. - 前記シールの径方向内端部にシールリップ部が形成され、
前記シールリップ部は、異物を留めるラビリンス空間を有することを特徴とする請求項１又は２に記載のシール付き転がり軸受。 A seal lip portion is formed at the radially inner end of the seal,
The rolling bearing with a seal according to claim 1 or 2, wherein the seal lip portion has a labyrinth space for holding foreign matter. - 自動車用ベルト式無段変速機で使用される請求項１～３のいずれか１項に記載のシール付き転がり軸受を使用したベルト式無段変速機。 4. A belt-type continuously variable transmission using the sealed rolling bearing according to claim 1, which is used in a belt-type continuously variable transmission for automobiles.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2015209297A JP2019023478A (en) | 2015-10-23 | 2015-10-23 | Sealed rolling bearing and belt type non-stage transmission |
| JP2015-209297 | 2015-10-23 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| WO2017069225A1 true WO2017069225A1 (en) | 2017-04-27 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| PCT/JP2016/081209 WO2017069225A1 (en) | 2015-10-23 | 2016-10-21 | Sealed roller bearing and belt-type continuously-variable transmission |
Country Status (2)
| Country | Link |
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| JP (1) | JP2019023478A (en) |
| WO (1) | WO2017069225A1 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110094427A (en) * | 2019-06-10 | 2019-08-06 | 余姚市新丰轴承有限公司 | Novel high rotary speed deep groove ball bearing waterproof leakproof rouge sealing ring |
| CN112211899A (en) * | 2019-07-12 | 2021-01-12 | 斯凯孚公司 | Bearing unit with small cross section |
| US20220025931A1 (en) * | 2019-04-03 | 2022-01-27 | Bearingart | Rolling bearing having improved sealability |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002106582A (en) * | 2000-10-02 | 2002-04-10 | Nsk Ltd | Rolling bearing with sealing plate for transmission |
| JP2002266876A (en) * | 2001-03-07 | 2002-09-18 | Nsk Ltd | Rolling bearing |
| JP2004019722A (en) * | 2002-06-13 | 2004-01-22 | Nsk Ltd | Roller bearing |
| JP2010002017A (en) * | 2008-06-23 | 2010-01-07 | Jtekt Corp | Rolling bearing |
| US20120098205A1 (en) * | 2009-05-15 | 2012-04-26 | Schaeffler Technologies Gmbh & Co. Kg | Sealing assembly for a rolling bearing |
-
2015
- 2015-10-23 JP JP2015209297A patent/JP2019023478A/en active Pending
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2016
- 2016-10-21 WO PCT/JP2016/081209 patent/WO2017069225A1/en active Application Filing
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2002106582A (en) * | 2000-10-02 | 2002-04-10 | Nsk Ltd | Rolling bearing with sealing plate for transmission |
| JP2002266876A (en) * | 2001-03-07 | 2002-09-18 | Nsk Ltd | Rolling bearing |
| JP2004019722A (en) * | 2002-06-13 | 2004-01-22 | Nsk Ltd | Roller bearing |
| JP2010002017A (en) * | 2008-06-23 | 2010-01-07 | Jtekt Corp | Rolling bearing |
| US20120098205A1 (en) * | 2009-05-15 | 2012-04-26 | Schaeffler Technologies Gmbh & Co. Kg | Sealing assembly for a rolling bearing |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20220025931A1 (en) * | 2019-04-03 | 2022-01-27 | Bearingart | Rolling bearing having improved sealability |
| US12006980B2 (en) * | 2019-04-03 | 2024-06-11 | Bearingart | Rolling bearing having improved sealability |
| CN110094427A (en) * | 2019-06-10 | 2019-08-06 | 余姚市新丰轴承有限公司 | Novel high rotary speed deep groove ball bearing waterproof leakproof rouge sealing ring |
| CN112211899A (en) * | 2019-07-12 | 2021-01-12 | 斯凯孚公司 | Bearing unit with small cross section |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2019023478A (en) | 2019-02-14 |
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